Diaphragm valve structure and thermal isolation method thereof

ABSTRACT

A diaphragm valve structure having application in diaphragm valves made completely from fluororesin at an operating temperature of 200° C. The diaphragm valve uses a thermal isolation method that consists of a heat transfer limiting structure and a heat dissipating structure, ensuring rigidity of the gas cylinder structure. The heat transfer limiting structure uses lattice-shaped ribbed plates with horizontal openings, wherein the lattice-shaped ribbed plates and a minimum diameter area of an annular portion are all provided with heat transfer section thickness. The heat dissipating structure consists of a multilayered structure for a preferred external natural cooling, and further using a coolant gas ensuring that the peripheral portion of the diaphragm and gas-tight sealing components on the valve shaft are sufficiently cooled.

BACKGROUND OF THE INVENTION (a) Field of the Invention

The present invention relates to a diaphragm valve structure and thermalisolation method thereof, and more particularly to a diaphragm valvemade from fluororesin that achieves an extremely low heat transfercoefficient of approximately 0.25 W/(mK), which is far below that ofceramic aluminum oxide (Al₂O₃) that achieves a heat transfer coefficientof 30 W/(mK). Such an extremely low heat transfer characteristic enablesthe fluororesin material to withstand an operating environment at a hightemperature of 250° C. However, the diaphragm valve must withstand highpressure, and currently only has application in a high corrosiveenvironment at a high temperature less-than 160° C. In order to achievethe capability for application in an operating environment at a hightemperature of 250° C., the diaphragm must be supported by metallicstructural components. Nonetheless, in actual practice, a metal ballvalve with a fluororesin inner lining can also be used at a hightemperature of 200° C. and in a high corrosive environment, clearlyrevealing that requiring a diaphragm valve made completely fromfluororesin in an operating environment at a high temperature of 200° C.and in a high corrosive environment is still a huge challenge.

(b) Description of the Prior Art

Diaphragm valves of the prior art use sealing and joining of a diaphragmmade from fluororesin to a valve body, and through combined driving of avalve shaft and separation from a corrosive liquid, corrosion resistantdiaphragm valves of the prior art have widespread application. Moreover,various types of structures have been developed for a variety ofapplication needs are suitable for a plurality of applications operatingat middle and low temperatures less than 160° C. and in a high corrosiveenvironment.

Diaphragm valves of the prior art are generally provided with one or anumber of the following characteristics:

1. Use of a piston of a high pressure gas actuated valve shaft as aswitch;

2. Hand-operating mechanism;

3. Use of an electric mechanism as a switch;

4. Use of a mechanism to regulate flow;

5. Removes static electricity produced by channeling liquid;

6. Use of metallic bolts to tightly lock a valve body;

7. Use of non-metallic screw threads to tightly fasten a valve body;

8. Structures that do not release particles;

9. Prevents structural creeping;

10. Leakage detection.

Diaphragm valves made from fluororesin of the prior art are assembledfrom a valve portion and an actuation gas cylinder. The valve portioncomprises components including a valve body and a diaphragm, while theactuation gas cylinder comprises components including an upper valvebody, a valve upper cover, and a valve shaft. The valve body comprises asquare portion and an annular portion. An actuation gas cylinder of theprior art assembled from the upper valve body and the valve upper coveris used to contain the components including the valve shaft, a piston,and a spring. And high pressure to drive gas on the reverse side of thespring force to drive switching of the diaphragm. The actuation gascylinder also comprises a gas cylinder structure, which, according toapplication use, can be separated into use in non-metallic diaphragmvalves and metallic diaphragm valve; or, according to structure,separated into non-metallic normally closed diaphragm valves,non-metallic normally open diaphragm valves, metallic normally closeddiaphragm valves, and metallic normally open diaphragm valves. Threadedteeth are used as the tight locking method between the valve body, uppervalve body, and valve upper cover of the non-metallic diaphragm valve;and is most suitable for use with extremely clean fluid channeling. Eachof the four corners of a metallic gas cylinder structure is tightenedand sealed using a metal bolt, which tightens and seals together thevalve body, upper valve body, and valve upper cover. Each of the boltsis protected by an upper bolt sleeve and a lower bolt sleeve thatprotect the valve body. The upper bolt sleeve is positioned on anexternal ring surface of the valve upper cover; the lower bolt sleeve ispositioned on an external ring surface of the upper valve body. A firstsealing face is positioned between the upper bolt sleeve and the lowerbolt sleeve, and a second sealing face is also positioned between thelower bolt sleeve and the annular portion of the valve body. Diaphragmsof the prior art are installed on the inner side of the valve bodyopening, and a peripheral portion of the diaphragm is tightened inside aseal groove by the upper valve body. A valve shaft set structureinstalled inside the gas cylinder structure comprises componentsincluding the diaphragm, the valve shaft, and the upper valve body; andcan be separated into a normally closed valve shaft set and a normallyopen valve shaft set. The upper valve body is normally used fortightening and fixing the valve shaft set of the metallic diaphragmvalve; and external threaded teeth of the upper valve body are normallyused for tightening and fixing the valve shaft set of the non-metallicdiaphragm valve; while some use a radial protruding edge of the uppervalve body for tightening and fixing. The gas chamber of the gascylinder structure of the prior art is installed inside the upper valvebody or the valve upper cover. When the piston is performing up and downreciprocating motion in the gas chamber, the upper valve body mustsustain multiple vibrations and considerable gas chamber stress, whicheasily cause bending of the valve shaft, resulting in the diaphragmleaking. Positions of the lower bolt sleeves of the second sealing faceare close to the outer edge of the diaphragm, which also result in theworrying problem of two-way permeation contamination, meaning themanufacturing engineer needs to constantly pay attention to thecorrosion condition of the metal bolts.

General specifications of diaphragm valves of the prior art:

Operating temperature: less than 80° C.; a few specially designeddiaphragm valves can operate at less than 160° C.

Normal temperature pressure rating: 3 kg/cm², 5 kg/cm².

When a special design is used for the diaphragm and the valve bodystructure has additional thickness, then normal temperature pressurerating can reach 7 kg/cm². In other words, none of the diaphragm valvesof the prior art can satisfy the requirements for application at anoperating temperature of 200° C.

The amount of heat transfer of fluororesin is equals a multiplicationproduct of its heat transfer coefficient, surface heat transfer, andtemperature gradient. An extremely low heat transfer coefficient ofapproximately 0.25 W/(mK) provides a viable condition for hightemperature operation using fluororesin. The greater the surface heattransfer, the greater the amount of heat transferred and the higher thetemperature of the entire structure of the diaphragm valve. The higherthe temperature gradient, the greater the amount of heat transferred,and the higher the temperature gradient represents a greater number ofnormal temperature areas on the entire structure of the diaphragm valve.Such normal temperature structures are able to provide a preferredstructural strength, however, they need greater heat dissipation inorder to maintain a normal temperature structure and provide structuralstrength. Heat source areas of the diaphragm valve include a valve boxheat source area, flow channel heat source area, inlet pipe heat sourcearea, outlet pipe heat source area, inlet connection heat source area,and an outlet connection heat source area. A high temperature liquidpasses through pipes, the valve structure, and the diaphragm, and isthen transmitted outward. The peripheral portion of the diaphragm isclose-fitting to the flow channel heat source area, the tighteningportion of the valve body and the upper valve body are the main pathsfor outward heat transmission from the heat source areas. The squareportion has a thick structure at the upper side of the inlet pipe, whichbecomes one of the main paths for outward heat transmission to the gascylinder structure. Diaphragm valve structures of the prior art guideand continue to accumulate heat inside the diaphragm valve, which causesthe entire structure to be at a high temperature and reduces thetemperature gradient; moreover, is unable to maintain structuralstrength. Sealing components such as a fluororesin O-ring are unable toavoid the danger of high temperatures, and can only be used at anoperating temperature less-than 160° C.

Regarding diaphragm valves that are able to operate at temperatures of200° C., their structure must satisfy the following four requirements.First, the structure must deal with heat source separation of aplurality of heat source areas using a heat transfer limiting structureand a heat dissipating structure. The heat transfer limiting structureplaces a restriction on the heat transfer section thickness of thestructure to form a heat transfer restriction area. The heat dissipatingstructure consists of natural cooling and internal cooling, by which theheat dissipating structure is able to reduce transmission of heat fromthe heat source areas to the structure, and provides a high temperaturegradient to maintain structural strength. The problems of heat sourceseparation are described below:

Problem 1: Heat transfer restriction. Surface heat transfer refers tostructural sectional areas of heat transfer paths of the heat sourceareas, which must be restricted to achieve the object of reducing theamount of heat transferred. The heat source areas transmit heat througha square plate, accumulated thickness, flow channel side wall, andperpendicular ribbed plates of the square portion, and then transmittedto the annular portion and the upper valve body, which results in aneven greater amount of heat being transmitted to the gas cylinderstructure. The central portion of the diaphragm has a large area thatabsorbs and channels heat into liquid, and a large amount of heat istransmitted to the valve shaft; moreover, accumulated thickness on theupper side of the inlet pipe has a large surface heat transfer thatcauses direct transmission of heat from the outlet heat source areas andthe inlet heat source areas to the square plate, the annular portion,and the upper valve body. The annular portion and the upper valve bodyboth have a large surface heat transfer area that form the main pathsfor heat transfer. The inlet and outlet pipe connections are alsoconnected to the accumulated thickness areas, and the four bolts alsohave substantial thickness and area that produce large heat transfer;moreover, the four metal bolts themselves are also good conductors forheat transmission.

Problem 2: Natural cooling. The external structure surface must havesufficient natural cooling, otherwise, it is unable to provide asufficient heat dissipating capacity to maintain a temperature gradientand structural strength. In particular, hot gas in the interior of thesquare portion is unable to dissipate outward, and only allows a largeamount of heat to transmit upward to the annular portion, whereupon theheat passes therethrough and transmitted to the large sectional area ofthe upper valve body.

Problem 3: Internal cooling. The diaphragm is close-fitting to the heatsource areas; moreover, the peripheral portion of the diaphragm isclose-fitting to the annular portion and becomes a heat centralizedarea, which is a position that easily distorts resulting in leakage. Thecentral portion of the diaphragm has a large area that absorbs andchannels heat into liquid, with a large amount of heat being transmittedto the valve shaft. A coolant gas is drawn in externally and mustsatisfy the cooling requirements of the peripheral portion of thediaphragm and the valve shaft. In addition. there is also the problemsof the structures of the valve portion and the actuation gas cylinderhaving to sustain pressure and a reciprocating motion of the piston,including the problems of surrounding corrosive gas, all of which resultin sealing failure. These problems are described below:

Problem 4: Tightening and sealing. As for the three above mentionedproblems of structural strength, reciprocating motion of the piston, andenvironmental corrosive gas; first, regarding structural strength, thegas cylinder structure and the valve body are subjected to thetightening force of the four metal bolts to effect sealing thereof.However, when the structural strengths of the components themselves areinadequate then structural creeping occurs. For example, when thethickness of the structures is too thin, high temperatures will resultin structural distortion, which greatly reduces the tightening force ofthe bolts causing the diaphragm to leak. Regarding reciprocating motionof the piston, the reciprocating motion of the piston, counteractingforces of springs, and actuation gas pressure are all sustained by thegas cylinder structure; moreover, acting forces will directly be appliedto the upper valve body and then transmitted to the valve body, whichwill impact the tightening force on the diaphragm. In addition, theeffect of vibration on the gas cylinder structure and the valve bodywill also result in structural creeping and distortion, which willreduce the tightening force of the bolts. And reduction in thetightening force on the peripheral portion of the diaphragm will resultin leakage. Regarding corrosion by the surrounding gas, the fourtightening bolts are protection of by bolt sleeves, however, highpenetrability of corrosive gas will still intrude into the first sealingface and the second sealing face of the bolt sleeves, resulting indamage to the bolts and reducing the tightening force thereof. Inparticular, the position of the second sealing face of the bolt sleevesis close to the outer edge of the diaphragm, which will greatly increasethe risk of the bolts becoming eroded and the worrying problem oftwo-way permeation contamination.

Accordingly, with continued operation in an operating environment at ahigh temperature of 200° C., the diaphragm valve will inevitablyencounter the above-described problems 1 to 4. The following describesthe problems regarding other important requirements:

Problem 5: Vibration damper device. Reciprocating motion of the pistonand the counteracting forces of springs produces vibration, and after along period of operation, structural creeping and distortion will causereduction in the degree of tightness in the structure. Hence, numerousprior art technologies use springs or vibration damping rubber to reducevibration to prevent leakage in the diaphragm; moreover, reducingvibration also decreases production of friction particles.

Problem 6: Friction particles. Concentricity and perpendicularity of thevalve shaft must be ensured, especially when operating at 200° C., so asto ensure a frontal surface press connection between the diaphragm andthe valve seat with no friction therebetween, thus, safeguarding againstparticles being produced. In addition, structural distortion of thevalve body, upper valve body, and valve upper cover results in the valveshaft being unable to maintain concentricity and perpendicularity, and afrontal surface press connection cannot be effected between thediaphragm and the valve seat, causing friction therebetween and theproduction of friction particles. Hence, numerous prior art technologiesadopt vibration damping methods to resolve such problems.

Problem 7: Eliminating static electricity. The problem of anaccumulation of static electricity in both the valve body and thediaphragm occurs when channeling nonconducting liquid; when the problembecomes serious, discharge sparks will damage the diaphragm. Hence,numerous prior art technologies use conducting material attached to anon-liquid contact side of the diaphragm to conduct away the accumulatedstatic electricity, thereby preventing damage to the diaphragm occurringdue to electric discharge.

Reference Example 1

With reference to the 2009 Japanese Patent No. JP2009002442 (A), whichdescribes a Fluid Control Valve, the contents of this reference example1 is provided in a similar vein and describes a diaphragm valveoperating at a temperature 160° C. Referring to FIG. 6A and FIG. 6B,which show a diaphragm valve 9 of the prior art made from fluororesin,wherein the diaphragm valve 9 is a metallic normally closed diaphragmvalve that is provided with a normally closed valve shaft set 961 (seeFIG. 6C), which is assembled from a valve portion 90 a and an actuationgas cylinder 90 b. The valve portion 90 a and the actuation gas cylinder90 b assume square shapes, however, the internal portions of both assumea circular structure. A bolt hole is provided in each of the four cornerportions, and metal bolts are used to secure screw tight connections andmaintain gas tightness. The metal bolts are respectively installed inthe interior of bolt sleeves, and the bolt sleeves are separated intoupper bolt sleeves and lower bolt sleeves. An upper sealing face isprovided between the upper bolt sleeves and the lower bolt sleeves;moreover, a lower sealing face is provided between the lower boltsleeves and the valve portion. The valve portion 90 a comprisescomponents including a valve body 91, a diaphragm 92, and a mountingplate. The actuation gas cylinder 90 b comprise the components includingan upper valve body 93, a valve upper cover 94, and a valve shaft 95.

The problems that need resolving in the present reference example 1involve improving the rigidity of the valve body 91, because under ahigh operating temperature, the valve body 91 being subjected topressure at an inlet pipe and an outlet pipe will distort; inparticular, the sealing portion position of the diaphragm 92 is unableto maintain a circular shape, resulting in leakage, see FIG. 11 of theFluid Control Valve invention of the prior art as disclosed in JapanesePatent No. JP2009002442 (A).

The valve body 91 is fitted with an inlet pipe 911, an outlet pipe 912,a valve box 913, an annular portion 915, and a square portion 916. Thediaphragm 92 is fitted with a peripheral portion 921, an elastic strip922, and a central portion 923. The upper valve body 93 is provided withan external ring surface 931, an internal ring surface 932, a lowersealing face 933, a tightening portion 934, a shaft hole portion 935,and a diaphragm chamber 936. The valve upper cover 94 is fitted with aninternal holding chamber 941, a top portion 942, an external ringsurface 943, and an upper sealing face 944. The valve shaft 95 is fittedwith a threaded teeth portion 951, a shaft rod 952, and a piston portion953. The valve box 913 is fitted with a valve seat 9131, a flow channel9132, a seal groove 9133, and a flow channel side wall 9134. The uppervalve body 93 and the valve upper cover 94 construct a gas cylinderstructure, which contains a gas chamber therein. The gas chamber isseparated by the piston 953 portion to form an upper gas chamber and alower gas chamber.

The peripheral portion 921 of the diaphragm 92 is fixed in the sealgroove 9133 on the upper edge of the flow channel side wall 9134, whichenables complete sealing of the entire valve box 913. The centralportion 923 corresponds to the valve seat 9131 and acts as a switch. Thelower sealing face 933 is positioned adjacent to the upper side of theperipheral portion 921 of the diaphragm 92.

The upper valve body 93 is installed between the annular portion 915 ofthe valve body 91 and the valve upper cover 94. The upper valve body 93assumes a central, convex, open cup-shaped structure, wherein theinternal ring surface 932 of the upper valve body 93 is fitted with agas chamber 937, which is used for coupling with the piston portion 953of the valve shaft 95. The outer edge of the bottom portion of the uppervalve body 93 is fitted with the tightening portion 934, which is usedto tighten the peripheral portion 921 of the diaphragm 92; moreover, thebottom portion forms a conical form, from which protrudes to form thecentrally positioned shaft hole portion 935, and a square form below theconical form forms the diaphragm chamber 936. The shaft hole portion 935is used to contain the valve shaft 95, and the external ring surface 931is fitted with an actuation gas connection 171.

The valve upper cover 94 assumes an inverted cup shape assembled on theupper valve body 93. The upper valve body 93 and the internal holdingchamber of the valve upper cover 94 construct the gas cylinder structureand an actuation gas cylinder. As well as being used to contain thecomponents including the valve shaft 95, the piston 953, and springs 12.

An inlet pipe connection installed on a side wall of the square portion916 connects to the inlet pipe 911, which horizontally penetrates thesquare portion 916 and then bends through an angle to form a rearopening in the center of the valve seat 9131 of the valve box 913, whichis used to join with the central portion 923 of the diaphragm 92,

The opening of the outlet pipe 912 is configured at the flow channelside wall 9134 and penetrates another side outer wall of the squareportion 916 to connect to an outlet pipe connection.

The periphery of the valve seat 9131 in the interior of the valve box913 forms a circumferential symmetrical, indented flow channel 9132. Thehighest area of the flow channel 9132 is positioned above the horizontalinlet pipe 911, two sides of which arc downward as hollows and extendaround the valve seat 9131, with the lower-most point connecting to alow side of the internal diameter of the horizontal outlet pipe 912. Anupper edge of the flow channel side wall 9134 is provided with the sealgroove 9133, which connects with the annular portion 915.

An opening is formed in the middle of a square plate 9161 of the squareportion 916 that is used to contain the valve box 913. the square plate9161 connects to the flow channel side wall 9134 and also connects tothe lower edge of the annular portion 915. Apart from being configuredwith a square cylindrical outer wall extending downward from the lowerside of the square plate 9161, the lower inner side of the square plate9161 is also fitted with lattice-shaped, longitudinal, vertical ribbedplates 9162 with lower side openings. The square plate 9161, the annularportion 915, and the valve box 913 extend upward from the bottom portionof the openings. These longitudinal vertical ribbed plates 9162perpendicularly cross over the lower side of the square plate 9161.

The inlet pipe 911, the outlet pipe 912, and the valve box 913 constructa structural support, and a square portion of the structural support isnamed a first molded square portion. Because the valve body 91 is formedby ejection or extrusion molding using PFA (PolyFluoroAlkoxy), theribbed plates 9162 are formed using slide blocks from the bottomportion, therefore, the upper sides of the inlet pipe 911 and the outletpipe 912, starting from the spaces between a horizontal center line tothe square plate 9161 are filled with PFA material. The PFA materialaccumulation is named the accumulated thickness 9163 and directlyconnects with the square plate 9161, the flow channel side wall 9134,the seal groove 9133, the inlet pipe 911, and the outlet pipe 912. Whenthe inlet pipe 911, the outlet pipe 912, and the valve box 913 are fullwith high temperature, high-pressure liquid causing distortion, thesquare plate 9161 must also distort along therewith, therebyconnectively affecting roundness of the flow channel side wall 9134, andconsequently affecting the gas-tight seal of the diaphragm 92. The lowerside of the annular portion 915 is installed on the square plate 9161and also positioned at the outer side of the seal groove 9133 of thevalve box 913; moreover, a sealing face 9151, the external ring surfaces931, 943 upwardly extend from the annular portion 915 and includeopening portions and breathing holes 9155. The annular portion 915provided with the breathing holes 9155 above the seal groove 9133 areused to satisfy the breathing needs of the diaphragm 92 when opening andclosing. The height of the annular portion 915 only satisfies the needsof the seal groove 9133 and the breathing holes 9155, to enable theannular portion 915 and the valve box 913 to construct a cup-shapedstructure. The opening portion of the cup-shaped structure is madegastight by the diaphragm 92, and the cup-shaped structure contains ahigh temperature liquid and is able to withstand the liquid pressuretherefrom. The outer edge of the cup-shaped structure forms the annularportion 915, and an outer edge height is provided between the annularportion 915 and the peripheral portion 921; for example, the outer edgeheight of an one inch opening diameter diaphragm valve is approximately6 mm. Regarding the cup-shaped structure, because it is a shallow cupshape, when the valve box 913 is subjected to high temperature and highpressure liquid, because the peripheral portion 921 of the diaphragm 92is assembled next to the outer edge of the cup-shaped structure, thus,the peripheral portion 921 very easily distorts causing leakage.Furthermore, because the outer edge height is only approximately 6 mm,it is unable to provide sufficient structural strength, and the additionof the high temperature and high pressure stress causes the inlet pipe911, the outlet pipe 912, and the accumulated thickness 916 to distort,as a consequence, the seal groove 9133 very easily leaks. In practice,the breathing holes 9155 are sometimes used to detect leakage. see FIG.11 of the Fluid Control Valve invention of the prior art as disclosed inJapanese Patent No. JP2009002442 (A).

The structure of the valve shaft set 961 comprises components includingthe diaphragm 92, the valve shaft 95, and the upper valve body 93,wherein the shaft rod 952 passes through the shaft hole portion 935 ofthe upper valve body 93, and the threaded teeth portion 951 is used asthe tight fastening method. a gas-tight sealing fluororesin O-ring isfitted on the shaft hole portion 935, and is used to prevent liquidleaking therefrom when the diaphragm 92 is damaged, as well as providingthe gas cylinder structure with a gas-tight seal. The piston portion 953is positioned at the upper side of the upper valve body 93 and is joinedto the shaft rod 952. The outer edge of the piston portion 953 is fittedwith the fluororesin O-ring connects and seals a gas chamber 90 d, andalso separates it into an upper gas chamber and a lower gas chamber.When any one of the gas chambers is full of gas, then the piston portion953 is driven by the high pressure gas and performs a correspondingmovement along with the internal ring surface 932. Moreover, because ofthe force and pressure of actuation gas imposed on and sustained by thepiston portion 953, the upper valve body 93 can also possibly distort,resulting in deviation in concentricity and perpendicularity of thevalve shaft 95. And because the upper valve body 93 is assembled on thesealing face 9151 of the annular portion 915, the serviceable life ofthe diaphragm 92 could even be reduced.

Referring to FIG. 6C, which shows a schematic view of heat source areasof the valve body 9, wherein the heat source areas include a valve boxheat source area 140 a, a flow channel heat source area 140 b, an inletpipe heat source area 140 c, an outlet pipe heat source area 140 d, aninlet connection heat source area 140 e, and an outlet connection heatsource area 140 f. A high temperature liquid passes through pipes,structures, and the diaphragm 92, and then transmitted outward. Theperipheral portion 921 of the diaphragm 92 is close-fitted to the flowchannel heat source area 140 b. The annular portion 915 of the valvebody 91 and the tightening portion 934 of the upper valve body 93 areall the main paths for outward heat transmission from the heat sourceareas, resulting in the annular portion 915 and the peripheral portion921 of the diaphragm 91 become the positions most easily distorted byheat, resulting in leakage, whereby the heat passes through a heattransfer path 14, and then through the valve body 91, the upper valvebody 93, and the valve upper cover 94, resulting in reduction in thestructural strength and tightening force of the gas cylinder structure.

Referring to FIG. 6B and FIG. 6D, which show schematic views of heattransfer paths of the diaphragm valve 9, and descriptions of the heattransfer paths are provided below. Valve shaft heat transfer paths 141transmit heat from the valve box 913 directly to the central portion ofthe diaphragm 92 and then toward the valve shaft 95. Square plate heattransfer paths 142 transfer heat from the outlet pipe heat source area140 d and the inlet tube heat source area 140 c, then along theaccumulated thickness 9163, and from the flow channel heat source area140 b passes through the flow channel side wall 9134 and the seal groove9133, whereupon the heat is finally transmitted towards the annularportion 915 and the upper valve body 93. The inlet connection heatsource area 140 e and the outlet connection heat source area 140 f ofconnector heat transfer paths 143 transmit heat to the annular portion915 through the square portion 916. Annular portion heat transfer paths144 will upwardly transmit heat to the upper valve body 93 and the valveupper cover 94, and concurrently a portion of the heat will betransmitted from the upper valve body 93 to the shaft hole portion 935.Shaft hole portion heat transfer paths 145 branch off to the shaft holeportion 935 from the annular wall heat transfer paths 143, and thentransmitted to the valve shaft 95. Square portion heat transfer paths146 transfer heat from the outlet pipe heat source area 140 d and theinlet tube heat source area 140 c, then transmitted along thelongitudinal vertical ribbed plates 9162 to outside the square portion916. The thickness of the flow channel side wall 9134 is provided withthe seal groove 9133, and can also be assembled with a fixing ring ofhigher hardness, which enables the thickness of the flow channel sidewall 9134 to have an even greater transmission area that accentuates thequantity of heat in the square plate heat transfer path 142. Becauseeach of the heat source areas of the present reference example 1 has alarge heat transfer sectional area, an even greater amount of heat istransmitted to the entire diaphragm valve structure, which causes hightemperature structural creeping and distortion, as well as resulting inreduction in the tightening force of the four metal bolts.

Referring to FIG. 6E, which shows a schematic view of heat dissipationof the diaphragm valve 9, and descriptions of natural heat dissipationpaths are provided below. Square portion heat dissipation paths 151 ofthe valve portion 90 a dissipate heat through square portion ribbedplates 152, and the actuation gas cylinder is provided with upper valvebody heat dissipation paths 153 and valve upper cover heat dissipationpaths 154, which respectively dissipate heat through the upper valvebody 93 and the valve upper cover 94. using natural convection onexterior surfaces to dissipate heat; however, the heat dissipationeffectiveness is not noticeable. The square portion 916 is aperpendicular gastight structure, and the majority of heat source areasare positioned in the interior of the square portion 916, which meansits very difficult to dissipate the heat outward. The heat will passthrough the square plate 9161 and enter the annular portion 915 and thevalve shaft 95, thereby increasing the temperature of the upper valvebody 93, resulting in the tightening force of the four support bolts ofthe gas cylinder structure failing. The fluororesin O-rings on the valveshaft 95 and the piston 953 are also unable to maintain functionalitydue to wear and tear; moreover, concentricity and perpendicularity ofthe valve shaft 95 will be a problem. The tightening portion 934 is alsounable to produce an effective tightening force on the peripheralportion 921 of the diaphragm 92, resulting in leakage. In addition, theleaking liquid will pass through an adjacent lower sealing face and flowto the bolt sleeves and metal bolts producing a corrosion reaction, thereactants from which will diffuse and flow back to enter the flowchannel 9132 and contaminate the liquid.

The characteristics of the present reference example 1 include: theadded thickness of the upper edge of the flow channel side wall 9134passes through the center opening of the square plate 9161, and the sealgroove 9133 is provided in the upper edge of the flow channel side wall9134. The annular portion 915 connects with the external ring surface ofthe flow channel side wall 9134, and also connects to the upper surfaceof the square plate 9161, and a fixing groove provided in the peripheralportion 921 of the diaphragm 92 enables assembling a fixing ring ofhigher hardness. The fixing ring enables maintaining the roundness ofthe seal groove 9133 and also effectively sustains the tightening forceof the tightening portion 934, as well as increase the supporting forceby means of the thick wall of the flow channel side wall 9134 andstabilize the peripheral portion 921 of the diaphragm 92 so as not to beaffected by high temperature distortion. The characteristics of thepresent invention 1 substantially improve on problems related to hightemperature distortion of the outer edge of the cup-shaped structure ofthe valve body 91 and leakage from the peripheral portion 921, toachieve application at an operating temperature reaching as high as≤160° C., see FIG. 3 of the Fluid Control Valve invention of the priorart as disclosed in Japanese Patent No. JP2009002442 (A).

A fixing ring of higher hardness is assembled on the peripheral portion921 of the diaphragm 92 of the present reference example 1, however, thefixing ring only enables maintaining the roundness of the seal groove9133 at temperatures below 160° C., and does not resolve the problem ofthe valve body 91 being subjected to the pressure at the inlet pipe 911and the outlet pipe 912, resulting in distortion. When the inlet pipe911 and the outlet pipe 912 are full with high temperature, highpressure liquid causing distortion thereof, consequently, the squareplate 9161 will also be distorted accordingly by the inlet pipe 911 andthe outlet pipe 912, thereby connectively affecting roundness of theflow channel side wall 9134, and affecting the gas-tight seal of thediaphragm 92. When the temperature exceeds 160° C. up to a temperatureof 200° C., the above-described distortions become more severe andgas-tight seals cannot be maintained.

Referring to FIG. 6F, which shows the structure of another referenceexample of the prior art that still has the valve body 91 but is notprovided with a complete structure for the square portion 916, and isnamed a second valve body, that is, the structure is only fitted withthe square plate 9161 that is provided with four bolt holes fortightening use. The outlet pipe 912, the inlet pipe 911, a flow channel,inlet connection, and an outlet connection are all partially exposed tothe exterior, and is named a second molded square portion structure.Moreover, the upper sides of the outlet pipe 912 and the inlet pipe 911are both next to the square plate 9161, and there still exists a largearea of the accumulated thickness 9163. This type of structure candecrease the inlet connection heat source area and the outlet connectionheat source area, and also adds to direct heat dissipation from externalsurfaces, which enable eliminating the problem of heat accumulating inthe square portion 916. However, the accumulated thickness area 9163still supplies a large surface heat transfer, with the heat beingtransmitted to the annular portion 915, the upper valve body 93, thevalve upper cover, and the valve shaft 95. This type of second moldedsquare portion structure still does not improve on existing problems,that is, the external edge height of the cup-shaped structure isapproximately 6 mm. which is unable to provide sufficient structuralstrength, with the cup-shaped structure lacking the support of squarelongitudinal vertical ribbed plates 9162. When the inlet pipe 911 andthe outlet pipe 912 are full with high temperature, high pressure liquidcausing distortion thereof, consequently, the square plate 9161 willalso be distorted accordingly by the inlet pipe 911 and the outlet pipe912, thereby connectively affecting roundness of the flow channel sidewall 9134, and affecting the gas-tight seal of the diaphragm 92. Hence,this type of structure only has application at relatively low operatingpressures and temperatures; for example, an operating pressure of 3kg/cm² and operating temperature of <100° C. If it is required tosatisfy a normal temperature and operating pressure of 5 kg/cm², thenthe thickness of the annular portion 915 must be increased and theexternal edge height of the cup-shaped structure raised. However, suchmodifications would result in the problem of a large heat transfer area.When assembling the pipe connections, the second valve body lacks thesquare portion 916 that facilitates fixing, thus, the degree ofdifficulty during the fixing operation will greatly increase duringconstruction.

Descriptions of Scenarios to Resolve the Above-Described Problems 1 to 4Using Reference Example 1:

Problem 1: Heat transfer restriction. A wide diameter channelaccumulated thickness area is reserved between the square plate and theinlet pipe and the outlet pipe. However, such a large heat transfer areawill result in substantial heat transfer to the annular portion and theupper valve body. Moreover, thickness of the flow channel side wall willalso substantially increase the heat transmission area. A fixing ringadditionally installed on the peripheral portion of the diaphragm willalso increase the heat transmission area, and the four metal bolts andbolt sleeves near to the annular portion will also transmit a largeamount of heat.

Problem 2: Natural cooling. Natural cooling is only provided usingsurface area natural cooling, with the upper valve body and the valveupper cover only providing surface area natural heat dissipation. Thelattice-shaped perpendicular ribbed plates of the first molded squareportion are completely unable to effectively dissipate heat, whichresults in a continuous accumulation of heat inside the diaphragm valvecausing the entire structure to be at a high temperature. Moreover, thelattice-shaped perpendicular ribbed plates of the second molded squareportion are completely unable to effectively dissipate heat.

Problem 3: Internal cooling. The structure lacks an internal mechanismfor the import of an external gas coolant, thus, the valve shaft set isnot cooled.

Problem 4: Tightening and sealing. The annular portion, the tighteningportion, the diaphragm peripheral portion, and the diaphragm center allhave heat being continuously transmitted therethrough. In addition, theheat is continuously accumulated inside the gas cylinder structure,causing the entire gas cylinder structure to be at a high temperature,resulting in an increase in structural creeping and distortion,consequently causing the four tightening metal bolts to become loose.The gas chamber is positioned on the valve body, and reciprocatingmotion of the piston together with the gas chamber pressure directlyapply force on the upper valve body, which easily cause the tighteningportion of the upper valve body to unable effectively tighten theperipheral portion of the diaphragm. The square plate tightly connectedto the inlet pipe and the outlet pipe still has an accumulatedthickness, thus, when the inlet pipe and the outlet pipe are full withhigh temperature, high pressure liquid causing distortion thereof, thesquare plate will also deform accordingly; moreover, roundness of theflow channel side wall cannot be maintained. Hence, the presentreference example only improves on distortion of the outer edge of thecup-shaped structure. In conclusion, the diaphragm valve is only able tooperate at temperatures below 160° C., and is unable to meet therequirements for operating at high temperatures less than 200° C. Thesecond valve body lacks the support of the ribbed plates of the squareportion, thus, the diaphragm is only able to satisfy the needs of anoperating environment at a normal temperature and operating pressure of3 kg/cm².

Reference Example 2

The 1996 Japanese Patent No. JPH08152078 (A) discloses a gas-OperatedValve, which is provided with a linear magnetic structure able to detectopening of a diaphragm. The structure in this reference patent issuitable for applications at normal temperature but is unsuitable forapplications at high temperatures. However, the exterior exposed pipeconnections of the structure have no inlet connection heat source areasor outlet connection heat source areas; the structure has relativelysmall inlet pipe heat source areas and outlet pipe heat source areas.Compared to other prior art structures, the present reference patent hasthe characteristic of having heat source areas that are relativelysmall. However, the inlet pipe and outlet pipe still have largeaccumulated thickness areas, which form heat transfer channels thatdirectly connect with the annular portion of the square plate. The uppervalve body of the present reference example uses threaded teeth totighten on the outer side of the annular portion of the valve body,which shrinks the heat transfer sectional area of the annular portion.An annular member used to securely fix the diaphragm is tightened on theinner side of the annular portion and has a large heat transfersectional area. The upper side of the diaphragm central portion alsostill has a large heat transfer area, that is, such a structure lacks aheat source separation design. The center of the valve upper cover isprovided with an actuation gas connection connected to actuation gasguide holes in the center of the valve shaft, which enable gas topenetrate into the interior of the gas cylinder and reach one side ofthe piston, which is used to drive the piston. However, the gas holesare not able to be used to satisfy the cooling requirements of the valveshaft, and the structure does not provide a design mechanism to carryout forced cooling. Regarding a heat dissipation mechanism, the valvebody is directly exposed to the gas to directly achieve natural cooling,but lacks a high temperature gradient design. The 1992 Japanese PatentNo. JPH04181079 (A) discloses a Pneumatic Operating Valve, which alsocomprises a similar valve shaft of the prior art fitted with actuationgas guide holes.

Descriptions of Scenarios to Resolve the Above-Described Problems 1 to 4Using Reference Example 2:

Problem 1: Heat transfer restriction. The annular portion and thediaphragm peripheral portion are separated, thus, the heat transmittedthrough the annular portion is not centralized in the peripheral portionof the diaphragm. The annular member used to securely fix the diaphragmstill has a large heat transfer area, and the upper side of thediaphragm central portion also still has a large heat transfer area,resulting in a large amount of heat being transmitted from thediaphragm.

Problem 2: Natural cooling. The diaphragm has the problem of a largetransmission of heat, and is only provided with surface natural coolingthat is unable to effect large heat dissipation to maintain atemperature gradient.

Problem 3: Internal cooling. The structure lacks a mechanism for theimport of an external gas coolant, and the actuation gas guide holes atthe shaft center only contribute to cooling the valve shaft, and do notcontribute to cooling the diaphragm.

Problem 4: Tightening and sealing. The annular member is fixedlytightened on the inner side of the annular portion, and is used totighten the peripheral portion of the diaphragm, which increases thetightening effectiveness of the upper valve body and reduces the affectof the reciprocating motion of the piston on the tightening of thediaphragm.

Reference Example 3

The 1997 Japanese Patent No. JPH09217845 (A) discloses a DiaphragmValve, and describes a normally closed diaphragm valve structureattached with shock absorbing springs. The structure in this referencepatent is suitable for applications at normal temperature but isunsuitable for applications at high temperatures. Normally closedsprings are fitted on the upper side of the piston to ensure thediaphragm is able to press down on the valve seat. And secondary springsfitted on the lower side of the piston enable the diaphragm to smoothlyclose when closing, which substantially reduce the possibility of thevalve seat producing friction particles.

The reference example 3 is suitable for use in normal temperatureapplications, and apart from resolving problems 1 to 4, it also resolvesthe above-described problems 5 and 6. Descriptions of scenarios toresolve problems 1 to 6 are provided below:

Problem 1: Heat transfer restriction. The structure has largeaccumulated thickness area; moreover, the inlet and outlet pipeconnections are also connected to the accumulated thickness area. Theannular portion is provided with an even larger heat transmission areaat the diaphragm peripheral portion. The thickness of the flow channelside wall also substantially increases the heat transfer area, and thefour metal bolts and bolt sleeves will also transmit a large amount ofheat. Under a high operating temperature, these heat areas transmit theheat to the upper valve body, reducing structural strength and producingserious structural creeping and distortion.

Problem 2: Natural cooling. The structure is only provided with externalsurface natural cooling, but with no specific cooling scenario, andlacks a high temperature gradient design.

Problem 3: Internal cooling. The structure lacks a mechanism for theimport of an external gas coolant,

Problem 4: Tightening and sealing. When used at normal temperatures, thestructure does not take into consideration the problem of continuousaccumulation of heat inside the diaphragm valve, and does not take intoconsideration high temperatures that results in the problem ofstructural creeping and distortion.

Problem 5: Vibration damper device. Reciprocating motion of the pistonand the counteracting forces of springs produce vibration, and after along period of operation, structural creeping and distortion will causereduction in the degree of tightness in the structure. The presentreference example 3 uses springs to reduce vibration to prevent leakagein the diaphragm; moreover, reducing vibration also decreases productionof friction particles.

Problem 6: Friction particles. The present reference example 3 does notuse any special design to prevent high temperature distortion of thevalve body, upper valve body, and valve upper cover, especially whenoperating at 200° C. Moreover, the structure is unable to ensureconcentricity and perpendicularity of the valve shaft to reduce frictionparticle production.

Reference Example 4

The 2015 Chinese Patent No. CN104633171 (A) discloses a Valve Apparatus,the structure of which is suitable for applications at normaltemperatures but is unsuitable for applications at high temperatures.The valve structure has conductive material installed in the valve shaftcenter, and the conductive material is able to contact channeling liquidto remove static electricity on the diaphragm. When the valve structureis channeling nonconducting high-purity water or other nonconductingliquid, the nonconducting diaphragm and valve body will accumulatefrictional static electricity; and when the high voltage staticelectricity on the diaphragm is discharged to the upper valve body, thediaphragm will be punctured and damaged. The conductive material on thevalve shaft is generally a heat conductor, which easily transmits heatfrom the valve box to other structures, and, thus, an imperfect heatsource separation design. The 2010 Japanese Patent No. JP2010121689 (A)discloses a Diaphragm Valve, which describes installing conductingmaterial on the diaphragm non-contact liquid side.

The structures of the above-described two reference patents are bothsuitable for applications at normal temperatures, and apart fromresolving the above-described problems 1 to 4, the structures alsoresolve problems 5 and 7. Descriptions of scenarios to resolve the aboveproblems are provided below:

Problem 1: Heat transfer restriction. Each of the structures has a largeaccumulated thickness area, and the inlet and outlet pipe connectionsare connected to the accumulated thickness area. The thickness of theflow channel side wall also substantially increases the heattransmission area. The diaphragm central portion also has a large heattransfer area.

Problem 2: Natural cooling. The structures are only provided withexternal surface natural cooling, with no specific cooling scenario, andlack a high temperature gradient design.

Problem 3: Internal cooling. The structures lack a mechanism for theimport of an external gas coolant.

Problem 4: Tightening and sealing. The upper valve body is tightlyscrewed onto the valve body, and the valve upper cover is tightlyscrewed onto the upper valve body. The upper valve body directlysustains the movement of the piston and the counteracting forces ofsprings, as well as high pressure actuation gas pressure, which willaffect the tightening force of the upper valve body on the peripheralportion of the diaphragm.

Problem 5: Vibration damper device. The upper valve body of the presentreference examples are installed with elastic rubber to reduce vibrationto prevent leakage in the diaphragm.

Problem 7: Eliminating static electricity. Conductive material installedin the valve shaft center is advantageous for the conduction of staticelectricity; however, the conductive material is disadvantageous forheat source separation. The static electricity channeling mode describedfor the Diaphragm Valve in Japanese Patent No. JP2010121689 (A) avoidsthe problem of heat transmission.

Reference Example 5

The 2003 U.S. Pat. No. 6,612,538 (B2) discloses a Two-way valve, thestructure of which is suitable for applications at normal temperaturesbut unsuitable for applications at high temperatures. The structuralmethod used in the present reference example 5 provides a metal threadon the center valve shaft, and uses the metal thread to firmly tightenthe diaphragm on the valve shaft. The two ends of the upper valve bodyare respectively provided with tight locking threaded teeth, which areused to tightly lock the upper valve body onto the valve upper cover andachieve connection therewith, thereby enabling the external surface ofthe valve to be absent of metal bolts and, thus, preventing corrosionfrom surrounding gas. The present reference example 5 is furtherinstalled with a rotatable annular member, which is used for assemblingan actuation gas connection, enabling the disposition of a high pressureactuation gas pipe even more convenient. The annular member enablesgas-tight sealing the valve body to the valve upper cover. The uppervalve body of the present reference example is installed with a shockabsorbing member to reduce vibration from piston movement to prevent theupper valve body from coming loose from the threaded teeth on the uppervalve body. The annular member installed on the present referenceexample is an important characteristic, however, in actual practice, thehigh pressure gas piping must be fixed to the surrounding gas pipe ductstructure. Moreover, these pipes are all configured in a fixeddirection, hence, such a structural device does not improve on thepracticality of a valve. In addition, additional gas-tight sealing isrequired, and, thus, disadvantageous for applications at hightemperatures; moreover, even the addition of more components will bringabout the risk of even more structural creeping. The outlet and inletpipes each have a large accumulated thickness area that form heattransfer channels directly connected to the annular portion of thesquare plate. Diaphragm outer O-rings are installed above the flowchannel side wall, and the upper valve body is locked tight on the innerside of the annular member and tightens the diaphragm outer O-rings. Inaddition, the outer O-rings on the outer side of the diaphragm each havea large heat transfer area, the metal thread on the valve shaft causesloss of heat source separation, and is unable to establish a hightemperature gradient. The annular portion of the valve body and thetightening portion of the upper valve body are the main heat sourceareas providing paths for outward heat transmission; moreover, theannular portion and the accumulated thickness area form heat transferchannels. Under a high operating temperature, these heat areas transmitthe heat to the upper valve body and reduce structural strength,producing serious structural creeping and distortion. The centralportion of the diaphragm has a large area that absorbs and channels heatinto a liquid, and a large amount of heat is transmitted to the valveshaft. The metal thread on the center valve shaft forms a channel forhigh-speed heat transfer. Fluororesin O-rings contact the valve shaft,which will cause the gas-tight seal function failing under conditions ofan operating temperature exceeding 160° C., and the center metal shaftis still the cause of a leaking diaphragm problem, resulting in metalliccorrosion and contamination problems. The peripheral portion of thediaphragm is a large heat source problem, with no specific coolingscenario, and is also unable to establish a high temperature gradient.

Descriptions of Scenarios to Resolve Problems 1 to 4 Using ReferenceExample 5 are Provided Below:

Problem 1: Heat transfer restriction. The structure has a largeaccumulated thickness area;

moreover, the inlet and outlet pipe connections are also connected tothe accumulated thickness area. The thickness of the flow channel sidewall will also substantially increase the heat transmission area. Theannular portion structure has a large heat transfer area, and thecentral portion of the diaphragm also has a large heat transfer area.

Problem 2: Natural cooling. The structure is only provided with externalsurface natural cooling, with no specific cooling scenario, and lacks ahigh temperature gradient design.

Problem 3: Internal cooling. The structure lacks a mechanism for theimport of an external gas coolant.

Problem 4: Tightening and sealing. The structure avoids using four metalbolts for lock tightening the exterior of the diaphragm valve that wouldsuffer from corrosion by surrounding corrosive gas, resulting in thethreads coming loose or even breaking, further resulting in aninadequate tightening force on the diaphragm valve and producingsubstantial leakage. The upper valve body is locked tight onto the valvebody, and the valve upper cover is locked tight onto the upper valvebody; moreover, the upper valve body directly sustains the movement ofthe piston and the counteracting forces of springs, as well as highpressure actuation gas pressure, which would affect the tightening forcefrom the upper valve body on the peripheral portion of the diaphragm.

A rotatable annular member is assembled between the valve body and thevalve upper cover, and the external ring surface of the upper valve bodyprovides gas-tight seal functions, which increases the risk of the uppervalve body loosening.

Reference Example 6

The 2014 Chinese Patent No, CN103717954 (A) discloses a Fluid controlvalve, the structure of which is suitable for applications at hightemperatures. The actuation gas cylinder of the present referenceexample 6 comprises an upper valve body, and this configuration is nameda gas cylinder body. The present patent is characterized in that: acontracted neck portion is configured between the gas chamber and thevalve body, and a butt connect surface is positioned between the valveportion and the actuation gas cylinder that is used to tighten theperipheral portion of the diaphragm. The butt connect surface at apartial portion of the valve body is named an annular portion. Thecontracted neck portion is configured on a contracted sectional area ofthe gas cylinder body, and a lower side of the contracted neck portionis configured with a disc-shaped flange, which is used to fix the valvebody and a metal mounting plate using metal bolts, enabling thediaphragm peripheral portion on the mounting plate and the disc-shapedflange to clamp down and maintain a tightening force. In addition, acoolant gas connection is assembled on the non-liquid contact side ofthe diaphragm, and connects to a gas vent of the gas cylinder through acenter hole of a shaft, the objective of which is to enable operation athigh temperatures ranging from 200° C. to 250° C. A preferred embodimentof the present reference example 6 is a valve portion made fromfluororesin, and apart from a gas-tight component, the actuation gascylinder is made from metal material. The heat energy produced by thevalve main body is limited to passing through the annular portion andtransmitting to the disc-shaped flange, and the heat transmission pathis further limited by the reduced sectional area of the contracted neckportion. Hence, heat cannot be effectively transmitted to the actuationgas cylinder, and with the addition of an external gas coolant, there isno worrying problem that the structure is unable to effectively ensurehigh temperature operation. Nonetheless, a large amount of structuralcreeping will occur using a valve portion made from fluororesin materialoperating at temperatures exceeding 200° C. However, the annular portionof the valve body is clamped by means of the mounting plate and thedisc-shaped flange, and metal bolts locking tight on the mounting plateare unaffected by high temperatures, thus, structural creeping producedby the valve body will not cause loosening of the metal bolts.

The first claim of the patent application of the present referenceexample 6 does not disclose use of metal materials. However, in actualpractice, the specification does not disclose a description of data thatenables a structure made completely from fluororesin material to achieveoperation at the alleged 250° C., because a large amount of structuralcreeping occurs when fluororesin reaches a temperature of 200° C.Moreover, a metal diaphragm valve with a contracted neck structure foruse at high temperatures is a commonly seen design in the prior art. The2001 US Patent No. US2001028049 (AI) discloses a High-temperature gascontrol valve, and the 2017 Taiwan Patent No. TW201702508 (A) disclosesa Diaphragm Valve. Both of these inventions describe similar contractedneck designs; moreover, the shaft center has actuation gas holes thatenable achieving a similar cooling effect.

The above-described reference example 6 that uses a structure madecompletely from fluororesin material still has the following problems:

Problem 1: Heat transfer restriction. The peripheral portion of thediaphragm is close-fitting to the flow channel heat source area,resulting in the seal groove of the annular portion and the periphery ofthe diaphragm both becoming positions most easily distorted by heat,causing leakage. Moreover, the annular portion of the valve body becomesa main path for transmitting heat, and the heat is accumulated on thenon-metal disc-shaped flange. Although the non-metal mounting plate isable to assist in maintaining a tightening force on the diaphragmperiphery, however, the risk of high temperature structural distortionresulting in leakage is still high. The contracted neck portion of theupper valve body provides a substantially effective heat transferrestriction area, which easily causes high temperature distortion of thefluororesin structure.

Problem 2: Natural cooling. The peripheral portion of the diaphragm isclose-fitting to the flow channel heat source area, resulting in theseal groove of the annular portion and the periphery of the diaphragmboth becoming positions most easily distorted by heat, causing leakage.The valve body and the upper valve body portions rely on surface naturalheat dissipation, and are unable to ensure structural strength of thecontracted neck portion made completely from fluororesin, as well asbeing unable to maintain concentricity and perpendicularity of the valveshaft.

Problem 3: Internal cooling. The structure is provided with a mechanismfor the import of an external gas coolant, a coolant gas connection isfitted on the non-liquid contact side of the diaphragm, and connects toa vent hole of the gas cylinder through a center hole of a shaft. Such aconfiguration is unable to provide further cooling for the peripheralportion of the diaphragm.

Problem 4: Tightening and sealing. The fluororesin disc-shaped flangeand non-metal mounting plate are able to sustain a greater amount ofheat before distorting. Hence, because of this, the lock tighteningbolts will become loose, and also cause reduction in the tighteningforce of the diaphragm peripheral portion. High temperatures will alsoenable back and forth vibration in the actuation gas cylinder todirectly cause structural distortion of the contracted neck portion.

Reference Example 7

The 2004 Japanese Patent No. JP2004019792A discloses a TRANSMISSION GASDISCHARGE STRUCTURE OF DIAPHRAGM VALVE, which resolves the problem of aninfinitesimal amount of fluid permeating and passing through thediaphragm, resulting in continuous accumulation on the backside of thediaphragm. However, this continuous accumulation of corrosive fluid willdamage the internal components of the valve. The structure in thepresent reference patent uses four lock tightening bolts that togetherlock tighten the valve body, upper valve body, and valve upper cover. Aninternal holding chamber of the valve upper cover is an actuation gascylinder, and is provided with an actuation gas connection. The pistonof the valve shaft performs a reciprocating motion in the gas chamberinner, the upper valve body is provided with two inter-connectingcleaning gas guide holes and connectors on the non-liquid contact sideof the diaphragm, wherein one of the connectors is an inlet connectorand the other is an outlet connector, which are able to eliminate theaccumulated permeating fluid. Reference example 7 only eliminates theaccumulated fluid on the backside of the diaphragm, but does not proposeany specific design for use in high temperature conditions. However, thedesign of cleaning gas guide holes can be used for cooling the diaphragmand valve shaft in high temperature applications. Nonetheless, thestructure still does not satisfy the cooling requirements of thediaphragm periphery. Because the position of the outlet pipe is higherthan the inlet tube, thus, the valve box is provided with a flow channeldesign, but uses added thickness to the annular portion. In addition,the inner side of the opening is provided with a seal groove, which isused to assemble the peripheral portion of the diaphragm that results ina large heat source from the valve box, which is transmitted upwardthrough the annular portion and the valve shaft.

When used at high temperatures, the above-described reference example 7still has the following problems:

Problem 1: Heat transfer restriction. The peripheral portion of thediaphragm is close-fitting to the flow channel heat source area,resulting in the seal groove of the annular portion and the peripheralportion of the diaphragm becoming the positions most easily distorted byheat and leaking. Moreover, the upper valve body has a large heattransfer area, which causes heat accumulation. Four metal bolts and boltsleeves also transmit a large amount of heat, thus, the risk of hightemperature distortion of the entire structure and leakage is stillhigh;

Problem 2: Natural cooling. The peripheral portion of the diaphragm isclose-fitting to the flow channel heat source area, resulting in theseal groove of the annular portion and the peripheral portion of thediaphragm becoming the positions most easily distorted by heat andleaking. The valve body relies on surface natural heat dissipation, andis unable to maintain structural strength of the annular portion at hightemperatures, and cannot sustain concentricity and perpendicularity ofthe valve shaft.

Problem 3: Internal cooling. The structure is provided with a mechanismfor the import of an external gas coolant, the upper valve body isprovided with two inter-connecting purgative gas guide holes andconnectors on the non-liquid contact side of the diaphragm, wherein oneof the connectors is an inlet and the other connector is an outlet,which are able to eliminate accumulated liquid that has permeated thediaphragm. This type of device has application for cooling the diaphragmand valve shaft, thereby reducing the temperature thereof. However, thestructure is unable to provide further cooling for the peripheralportion of the diaphragm.

Problem 4: Tightening and sealing. The annular portion is able tosustain a greater amount of heat before distorting, but is unable toestablish a high temperature gradient, and because of this, the locktightening bolts will become loose, and also cause reduction in thetightening force of the diaphragm peripheral portion,

From the above-described reference examples 1 to 7 and discussion ofproblems 1 to 4, diaphragm valves made from fluororesin material of theprior art are completely unable to satisfy requirements for operating atthe high temperature of 200° C., and the liquid channeling of corrosiveliquids, such as hydrofluoric acid, hydrochloric acid, sulfuric acid,and the like.

SUMMARY OF THE INVENTION

The present invention provides improvements on the shortcomings offluororesin material that easily causes structural creeping at 200° C. Adiaphragm valve made from fluororesin is assembled from a valve portionand an actuation gas cylinder, wherein the valve portion comprisescomponents including a valve body and a diaphragm. The actuation gascylinder comprises components including an upper valve body, a valveupper cover, a valve shaft, and part of a valve body structure. Theactuation gas cylinder further comprises a gas cylinder structure, andalso comprises an actuation gas connection and a coolant gas connection.The gas cylinder structure is assembled from the valve upper coverdisposed gastight on the valve body. The interior of the gas cylinderstructure contains components including a valve shaft set and springs,which construct the actuation gas cylinder. The gas cylinder structureis provided with a gas chamber, which is separated by a piston of thevalve shaft set into an upper gas chamber and a lower gas chamber. Thevalve shaft set structure comprises and is assembled from the diaphragm,the valve shaft, and the upper valve body. The tail end of the valveshaft penetrates a center through hole of the valve upper cover. Becauseof the different structures of diaphragm valves, the gas chamber isinstalled on an annular portion or the valve upper cover.

The valve body is provided with an inlet pipe, an outlet pipe, a valvebox, an annular portion, and a square portion.

Heat source areas of the diaphragm are positioned on the valve body andinclude a valve box heat source area, a flow channel heat source area,an inlet pipe heat source area, an outlet pipe heat source area, aninlet connection heat source area, and an outlet connection heat sourcearea. A high temperature liquid is outward transmitted through theoutlet pipe, the square portion, the annular portion, the upper valvebody, and the diaphragm.

The valve box comprises a valve seat and a flow channel. The diaphragmis provided with a peripheral portion, an elastic strip, and a centralportion. The peripheral portion enables completely sealing of the valvebox, and the central portion acts as a switch corresponding to the valveseat.

The valve shaft is provided with a locking portion, a hollow shaft rod,an axis hole, and a piston portion. The locking portion is used totightly lock the central portion of the diaphragm. The hollow shaft rodpasses through a shaft hole portion of the upper valve body, and issealed by a plurality of O-rings.

The annular portion forms an open ring structure, and comprises asealing face, an opening portion, an internal ring surface, a minimumdiameter area, and an external ring surface. The internal ring surfaceis provided with a seal groove and an O-ring groove,

The square portion comprises a square plate, a plurality of longitudinalvertical ribbed plates, a plurality of transverse vertical ribbedplates, and a plurality of horizontal ribbed plates, which construct alattice-shaped ribbed plate structure with horizontal openings. Thelongitudinal vertical ribbed plates are connected to the lower side ofthe square plate and the upper sides of the inlet pipe and the outletpipe, as well as connecting to the flow channel. An opening in themiddle of the square plate is used to contain the valve box and connectsto the side wall of the flow channel.

The upper valve body is provided with an external ring surface, aninternal ring surface, a tightening portion, the shaft hole portion, anda diaphragm chamber. The upper valve body is installed on the annularportion, and the tightening portion is used to tighten the peripheralportion of the diaphragm into the seal groove of the annular portion.The upper valve body is assembled on the internal ring surface of theannular portion, and assumes a central pyramidal, convex open cup-shapedstructure.

The valve upper cover is provided with an internal holding chamber, atop portion, a center through hole, the external ring surface, and asealing face. the valve upper cover is installed on the upper side ofthe annular portion.

The annular portion and the valve box construct a cup-shaped structure,the opening portion of which is made gastight by the diaphragm. Thecup-shaped structure contains a high temperature liquid and endures theliquid pressure therefrom. The cup-shaped structure assumes a deep cupshape, with a height range of the outer edge thereof achieving a heightof 80% to 160% of that of the upper valve body. Further, the diaphragmis assembled at a position close to the bottom portion of the cup-shapedstructure, wherein this position is also provided with a cooling flowchannel for cooling. Under conditions of high temperature distortion,the annular portion assists in providing high structural strength;moreover, the valve shaft set is assembled on the annular portion, thatis, the deep cup-shaped structure provides the valve shaft set with themost stable structural support. When the valve shaft is performing anopening/closing movement, concentricity and perpendicularity is ensured,which provides maximum assistance to reducing particle release.

The structural originality of the present invention is achieved throughthe structural innovation of the valve body, the gas cylinder structure,and the valve shaft set. The structural originality of the presentinvention is suitable for different types of diaphragm valve, such as anon-metallic normally closed diaphragm valve, non-metallic normally opendiaphragm valve, metallic normally closed diaphragm valve, metallicnormally open diaphragm valve, and an electrostatic dissipating normallyopen diaphragm valve, wherein the electrostatic dissipating diaphragmvalve uses a conductive fibre to penetrate the axis hole and clearancesof bolt holes. In addition, the conductive fibre is wound around in anannular curved line fashion and bonded to the diaphragm surface. Theconductive fibre inside the axis hole is in a fixed state and will notmove in correspondence with movement of the valve shaft.

A thermal isolation method of the present invention comprises a heattransfer restriction method and a heat dissipation method, which areused to separate the heat sources and reinforce heat dissipation toenable maintaining a structural temperature gradient. The heat transferrestriction method of the present invention restricts heat transferthrough sectional areas of the structure, hereinafter referred to asheat transfer restriction areas, which are used to reduce the amount ofheat being conducted through heat source areas and achieve the object ofheat separation.

The thermal isolation method is achieved using methods comprising aplurality of heat transfer restriction methods and a plurality of heatdissipation methods. The heat transfer restriction methods restrict heattransfer through heat transfer section thicknesses of the structure,which become the heat transfer restriction areas. Using a diaphragmvalve with a 1 inch opening diameter as an example, the heat transfersection thicknesses are 3 mm. The lattice-shaped ribbed plate structureof the square portion of the present invention is also a heat transferrestriction area. The external side wall of the seal groove of theminimum diameter area of the annular portion is the internal ringsurface of the annular portion, causing post-assembly of the diaphragmand the minimum diameter area to be essentially located at identicalhorizontal positions. The internal side wall of the seal groove is theside wall of the flow channel; and the bottom portion of the seal grooveis the square plate, all of which are the heat transfer restrictionareas. The external ring surface is fitted with a plurality ofperpendicular heat dissipation ribbed plates that connect with thesquare plate. The heat dissipation ribbed plates are provided with theheat transfer restriction areas. The gas cylinder structure comprises aportion of the annular portion and is positioned above the heat transferrestriction areas of the square plate and the annular portion. The gascylinder structure uses a plurality of bolt sleeves and a plurality ofmetal bolts for tightening and gastight sealing thereof. The boltsleeves and the metal bolts are positioned on the upper side of theminimum diameter area of the annular portion and the upper side of thesquare plate, as well as being positioned above the heat transferrestriction areas. When the coolant gas connection is installed on thevalve upper cover, a plurality of gas columns on the outer side of thegas cylinder structure are positioned on the upper side of the minimumdiameter area of the annular portion and the upper side of the squareplate, as well as being positioned above the heat transfer restrictionareas.

The heat dissipation method comprises an external natural coolingstructure and an internal cooling structure. The external naturalcooling structure comprises the lattice-shaped ribbed plate structure,ribbed plates of the annular portion, and ribbed plates of the valveupper cover, which provide natural-convection cooling. The internalcooling structure achieves a cooling effect using a coolant gas thatpasses through a gas coolant flow channel, which comprises one or morethan one coolant gas hole in the annular portion connected to a coolantgas ring groove. The coolant gas ring groove is further connected to aplurality of coolant gas guide holes in the tightening portion of theupper valve body. The coolant gas guide holes afford passage to thediaphragm chamber, and the coolant gas passes through the plurality ofcoolant gas guide holes that connect to the axis hole.

The internal natural cooling uses the rising force of the hightemperature coolant gas in the hollow shaft rod to assist the externalcoolant gas to enter the plurality of coolant gas guide holes of theannular portion to achieve the object of expelling the hot coolant gasfrom the hollow shaft rod. The internal forced cooling consists ofexternally forcing high pressure coolant gas from the coolant gasconnection to pass through the coolant gas guide holes to enter thecoolant gas ring groove, and then through the hollow shaft rod toachieve the internal forced cooling. The coolant gas passing through thecoolant gas ring groove of the annular portion passes through aplurality of the coolant gas guide holes of the upper valve body to coolthe peripheral portion of the diaphragm, and then flows through thediaphragm space of non-liquid contact to cool the diaphragm. The coolantgas then passes through the axis hole of the hollow shaft rod to carryaway the heat transmitted through the central portion of the diaphragm,which is used to ensure gas-tight sealing of the fluororesin O-rings andbe unaffected by high temperatures.

The annular portion and the peripheral portion of the diaphragm are thepositions most easily distorted by heat, resulting in leakage, thus,when the upper valve body is used to tighten the peripheral portion ofthe diaphragm into the seal groove of the annular portion. theperipheral portion is adjacent to the coolant gas hole. The cup-shapedstructure assumes a deep cup shape because the height range of the outeredge reaches 80% to 160% of the height of the upper valve body,moreover, the diaphragm is assembled at a position close to the bottomportion of the cup-shaped structure, wherein this position is alsoprovided with a coolant flow channel to effect cooling, thus, underconditions of high temperature distortion, the annular portion assistsin providing high structural strength. In addition, the valve shaft setis assembled on the annular portion, that is, the deep cup-shapedstructure provides the valve shaft set with the most stable structuralsupport. Hence, concentricity and perpendicularity is ensured when thevalve shaft is performing an opening/closing movement, and maximumassistance to reducing particle release is provided. The gas cylinderstructure is positioned above the heat transfer restriction areas of thesquare plate and the annular portion, and comprises a tightening andsealing device on the actuation gas cylinder and other components. Asfor the external natural cooling, the lattice-shaped ribbed platestructure of the square portion, and a plurality of the heat dissipationribbed plates of the external ring surface of the annular portionprovide substantial natural heat dissipation surfaces to maintain a hightemperature gradient. The multilayered ribbed plates with horizontalopenings is a structural characteristic of the present inventionproviding open ventilation, which is able to greatly facilitate naturalheat dissipation.

Regarding the internal cooling method, coolant gas in the coolant gasring groove passes through a plurality of the coolant gas guide holes ofthe upper valve body to cool the peripheral portion of the diaphragm,and then flows through the diaphragm space of non-liquid contact side tocool the diaphragm. The coolant gas then passes through the axis hole ofthe hollow shaft rod to carry away the heat transmitted through thecentral portion of the diaphragm, ensuring the gas-tight sealedfluororesin O-rings are unaffected by high temperatures and ensuringthat the entire fluororesin diaphragm valve has application attemperatures reaching as high as 200° C. During natural circulationcooling, the fluororesin diaphragm valve uses the rising force of thehot coolant gas within the hollow axis passage in the valve interior toguide the external gas to enter through one or more than one of thecoolant gas holes. During forced circulation cooling, a high pressurecoolant gas is supplied to enable improving dependability and durabilityfor application at temperatures reaching as high as 200° C. and in ahigh corrosive environment.

The present invention also provides a diaphragm valve structurecomprising a valve portion and an actuation gas cylinder, wherein thevalve portion comprises the fluororesin valve body and the fluororesindiaphragm. The actuation gas cylinder comprises the upper valve body,the valve upper cover, and the valve shaft. The valve body comprises theannular portion and the square portion. The square portion comprises afirst side surface, a second side surface, a bottom surface, the inletpipe, the outlet pipe, and the valve box. The valve box comprises thevalve seat and the flow channel. The diaphragm is provided with theperipheral portion, the elastic strip, and the central portion. Theupper valve body is installed on the annular portion and tightly locksthe diaphragm. The valve upper cover is disposed gastight on the valvebody to form the gas cylinder structure. The gas cylinder structure isprovided with the gas chamber, which is separated by the piston portionto form the upper gas chamber and the lower gas chamber. The valve shaftcomprises the tightening portion, which is used to tightly lock thecentral portion of the diaphragm. A plurality of the ribbed plates ispositioned on any one of, any two of, or all of the first side surface,the second side surface, and the bottom surface.

The present invention also provides a diaphragm valve structurecomprising the valve portion and the actuation gas cylinder, wherein thevalve portion comprises the fluororesin valve body and the fluororesindiaphragm. The actuation gas cylinder comprises the upper valve body,the valve upper cover, and the valve shaft, wherein the valve bodycomprises the annular portion and the square portion. The diaphragm isprovided with the peripheral portion, the elastic strip, and the centralportion. The upper valve body comprises the diaphragm chamber, and theupper valve body is installed on the annular portion and tightly locksthe diaphragm. The valve upper cover is disposed gastight on the valvebody to form the gas cylinder structure, which is provided with the gaschamber that is separated by the piston portion to form the upper gaschamber and the lower gas chamber. The valve shaft comprises thetightening portion, the hollow shaft rod, and the axis hole, wherein thetightening portion is used to tightly lock the central portion of thediaphragm. The hollow shaft rod is provided with a gas guide hole, whichaffords passage to the axis hole and also affords passage to thediaphragm chamber. The gas coolant flow channel is configured on theannular portion and links up with the diaphragm chamber.

The present invention also provides a diaphragm valve structurecomprising the valve portion and the actuation gas cylinder, wherein thevalve portion comprises the fluororesin valve body and the fluororesindiaphragm. The actuation gas cylinder comprises the upper valve body,the valve upper cover, and the valve shaft. The valve body comprises theannular portion and the square portion. The diaphragm is provided withthe peripheral portion, the elastic strip, and the central portion. Theupper valve body is installed on the annular portion and tightly locksthe diaphragm. The upper valve body comprises a first annular recess,and the valve upper cover is disposed gastight on the valve body to formthe gas cylinder structure, which is provided with the gas chamber thatis separated by the piston portion to form the upper gas chamber and thelower gas chamber. The valve shaft comprises the tightening portion, thehollow shaft rod, and a shock absorption ring. The tightening portion isused to tightly lock the central portion of the diaphragm, and the shockabsorption ring is correspondingly assembled on the above-describedfirst annular recess.

The present invention also provides a diaphragm valve structurecomprising the valve portion and the actuation gas cylinder, wherein thevalve portion comprises the fluororesin valve body and the fluororesindiaphragm. The actuation gas cylinder comprises the upper valve body,the valve upper cover, and the valve shaft. The valve body comprises theannular portion and the square portion. The connecting area between thesquare portion and the annular portion is provided with a minimumdiameter. The annular portion is provided with the internal ringsurface, which is configured with the seal groove that is positioned atthe minimum diameter area. The diaphragm is provided with the peripheralportion, the elastic strip, and the central portion. The upper valvebody is installed on the annular portion and is provided with thetightening portion, which tightly locks the peripheral portion on theposition of the seal groove. The valve upper cover is disposed gastighton the valve body to form the gas cylinder structure, which is providedwith the gas chamber that is separated by the piston portion to form theupper gas chamber and the lower gas chamber. The valve shaft comprisesthe tightening portion, which is used to tightly lock the centralportion of the diaphragm.

The present invention also provides a diaphragm valve structurecomprising the valve portion and the actuation gas cylinder, wherein thevalve portion comprises the fluororesin valve body and the fluororesindiaphragm. The actuation gas cylinder comprises the upper valve body,the valve upper cover, and the valve shaft. The valve body comprises theannular portion and the square portion, which comprises the valve box.The annular portion and the valve box construct a deep cup-shapedstructure. The diaphragm is provided with the peripheral portion, theelastic strip, and the central portion. The upper valve body isinstalled on the annular portion and tightly locks the diaphragm. Thevalve upper cover is disposed gastight on the valve body to form the gascylinder structure, which is provided with the gas chamber that isseparated by the piston portion to form the upper gas chamber and thelower gas chamber. The valve shaft comprises the tightening portion,which is used to tightly lock the central portion of the diaphragm. Theexternal edge height of the above-described cup-shaped structureachieves a height of 80% to 160% of that of the upper valve body.

Regarding proposed preferred strategies for the separation of heatsources to deal with the following problems 1 to 4, heat sourceseparation scenarios are described below that are able to satisfy therequirements of applications operating at temperatures reaching as highas 200° C.:

Problem 1: Heat transfer restriction. The flow channel side wall, thesquare plate, the upper valve body, and the annular portion are allconfigured with heat transfer restriction areas having cross-sectionalarea restriction. An inlet pipe connection, an outlet pipe connection,the inlet pipe, the outlet pipe, and the flow channel of the heat sourceareas are all supported by the lattice-shaped ribbed plate structure ofthe square portion, thereby limiting the heat transfer areas. Moreover,the outward transmission path of the heat is dispersed to the ribbedplates with horizontal openings. The bottom portions of the firstannular recess and the second annular recess are configured with heattransfer restriction areas, and heat transmitted outward from the heatsource areas is restricted by the heat transfer restriction areas andthus substantially decreased. Hence, this decrease in heat transferenables the achievability of natural heat dissipation through the heatdissipation ribbed plates and component surfaces.

Problem 2: Natural cooling. The valve body structure uses a lot ofnatural heat dissipation surfaces to maintain a high temperaturegradient. the multilayered lattice-shaped ribbed plate structure withhorizontal openings of the square portion is a structural characteristicof the present invention providing open ventilation, which is able togreatly facilitate natural heat dissipation and to sufficiently maintaina high temperature gradient, as well as enabling ensuring structuralstrength. When heat is transported to the annular portion, the heatdissipation ribbed plates of the external ring surface provides naturalheat dissipation.

Problem 3: Internal cooling. The gas coolant flow channel cools thediaphragm in the interior of the diaphragm valve and the valve shaft,and also strengthens the intrinsic heat source separation effect. Thegas used for forced circulation cooling or natural circulation coolingpasses through the gas ring groove, and then passes through a pluralityof the gas guide holes of the upper valve body to cool the peripheralportion of the diaphragm. The gas then flows through the non-liquidcontact side to cool the diaphragm, and finally through the gas guideholes of the hollow shaft rod to enter the center hole to carry away theheat transmitted through the central portion of the diaphragm, ensuringthe gas-tight sealed fluororesin O-rings are unaffected by hightemperatures, and ensuring that the entire fluororesin diaphragm valvehas application at temperatures reaching as high as 200° C. Methods forsupplying the gas include natural circulation cooling or external gasforced cooling.

During natural circulation cooling, the rising force of hot coolant gaswithin the hollow axis passage in the valve interior is used to guideexternal gas to enter through one or more than one of the gas guideholes.

During forced circulation cooling, high pressure coolant gas passesthrough a coolant gas connection as the supply entry point to enableimproving dependability and durability for application at temperaturesreaching as high as 200° C. and in a high corrosive environment.

Problem 4: Tightening and sealing. The valve body and the gas cylinderstructure and the structure of the valve shaft set meet the requirementsto provide high structural strength, resistance to surrounding corrosivegas, and endurance to the reciprocating motion of the piston.

Regarding the high structural strength, the square portion of the valveis provided with the lattice-shaped ribbed structure with horizontalopenings, which provide the structural strength and heat transferrestriction. The annular portion and the valve box construct thecup-shaped structure, which assumes a deep cup shape because the heightrange of the outer edge reaches 80% to 160% of the height of the uppervalve body, moreover, the diaphragm is assembled at a position close tothe bottom portion of the cup-shaped structure, wherein this position isalso provided with the coolant flow channel to effect cooling, thus,under conditions of high temperature distortion, the annular portionassists in providing high structural strength that is stronger comparedto the prior art. The valve shaft set is assembled on the annularportion, that is, the deep cup-shaped structure provides the valve shaftset with the most stable structural support. Hence, concentricity andperpendicularity is ensured when the valve shaft is performing anopening/closing movement, and maximum assistance to reducing particlerelease is provided. The gas cylinder structure is supported by thestructure of the annular portion, ensuring rigid support of the shafthole portion and ensuring perpendicularity and concentricity of thevalve shaft. The external ring surface fitted with heat dissipationribbed plates provides an additional supporting force for the gascylinder. The piston transfers the actuation gas pressure and springvibrations of the gas cylinder to the valve body, the structure of whichabsorbs and endures, thereby substantially reducing structural looseningresulting from the tightening force producing structural creeping.Moreover, the gas cylinder structure is positioned above the heattransfer restriction areas of the annular portion, and the upper valvebody is provided with the heat transfer restriction areas, which areable to minimize heat transmission of the heat source areas and maintainstrength of the gas cylinder structure.

Regarding resistance to surrounding corrosive gas, when using anon-metallic structure, the valve upper cover is tightly screwed ontothe valve body using threaded teeth, thus removing contaminationproblems from metallic oxides. When using a metallic structure, themetal bolts of the gas cylinder structure are protected by the boltsleeves; moreover, only one sealing face has the bolt sleeves, and theheight difference value between the sealing face and the peripheralportion of the diaphragm at least equals to more than 80% of the lengthof the upper valve body. When metallic oxides are diffusing everywhere,such a height difference is sufficient to isolate the contaminationpermeating problem, and eliminates the need for operators and inspectorsto inspect whether or not the bolts are corroded and need replacing,that is, even though the external surface of the valve body is subjectedto corrosion by the surrounding corrosive gas, the problem of reductionin the tightening force will not occur.

Regarding endurance to the reciprocating motion of the piston,reciprocating motion of the piston takes place in the gas chamber, andthe upper valve body is assembled on the internal ring surface of theannular portion; moreover, the valve body bears the acting force frommultiple movements of the piston, therefore, the upper valve body willnot distort and loosen. Further, the tightening force will not reducecausing in leakage from the diaphragm, thereby ensuring concentricityand perpendicularity of the valve shaft, and maintaining the tighteningforce on the peripheral portion of the diaphragm to minimize leakage andextend the serviceable life thereof.

To enable a further understanding of said objectives and thetechnological methods of the invention herein, a brief description ofthe drawings is provided below followed by a detailed description of thepreferred embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a cross-sectional view of a non-metal normally closeddiaphragm valve of a first embodiment of the present invention.

FIG. 1B is a three-dimensional external view of a metallic normally opendiaphragm valve of a second embodiment of the present invention.

FIG. 2A is a schematic view of valve body heat source areas of thepresent invention.

FIG. 2B is a schematic view of heat transfer paths of a diaphragm valveof the present invention.

FIG. 2C is a schematic view of natural heat dissipation paths of thediaphragm valve of the present invention.

FIG. 2D is a schematic view of internal cooling of the diaphragm valveof the present invention.

FIG. 3A is a three-dimensional cross-sectional view of a valve body ofthe present invention.

FIG. 3B is horizontal cross-sectional view of an inlet pipe positionedon the valve body according to the present invention.

FIG. 3C is an exploded three-dimensional cross-sectional view of asecond valve body of the present invention.

FIG. 4A is a cross-sectional view of a normally closed external threadedtooth bearing set of the present invention.

FIG. 4B is a cross-sectional view of a normally open external threadedtooth bearing set of the present invention.

FIG. 4C is a cross-sectional view of a normally closed protruding edgevalve shaft set of the present invention.

FIG. 4D is a cross-sectional view of a normally open protruding ringvalve shaft set of the present invention.

FIG. 4E is a cross-sectional view of a normally closed staticelectricity valve shaft set of the present invention.

FIG. 5A is a partial cross-sectional view of a gas cylinder structurepositioned on an annular portion gas chamber using the external threadedtooth bearing set according to the present invention.

FIG. 5B is a partial cross-sectional view of a gas cylinder structurepositioned on a valve upper cover gas chamber using the externalthreaded tooth bearing set according to the present invention.

FIG. 5C is a partial cross-sectional view of a gas cylinder structurepositioned on a valve upper cover gas chamber using a flange bearing setaccording to the present invention.

FIG. 6A is a cross-sectional view of a high temperature resistantdiaphragm valve of the prior art.

FIG. 6B is a horizontal cross-sectional view of a valve body of theprior art.

FIG. 6C is a schematic view of valve body heat source areas of the priorart.

FIG. 6D is a schematic view of heat transfer paths of a diaphragm valveaccording to the prior art.

FIG. 6E is a schematic view of heat dissipation of a diaphragm valveaccording to the prior art.

FIG. 6F is a cross-sectional view of a valve body of a diaphragm valveof the prior art that adopts a second molded square portion and ametallic annular portion.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

A thermal isolation method of the present invention comprises a heattransfer restriction method and a heat dissipation method, which areused to separate the heat sources and reinforce heat dissipation loss,thereby maintaining a structural temperature gradient. The heat transferrestriction method of the present invention restricts heat transferthrough section thickness areas of the structure, hereinafter referredto as heat transfer restriction areas 147, which are used to reduce theamount of heat being conducted through heat source areas to achieve theobject of heat separation.

Referring to FIG. 1A, FIG. 1B, FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D, FIG.3A, FIG. 3B, FIG. 3C, FIG. 4A, FIG. 4B, FIG. 4C, FIG. 4D, FIG. 4E, FIG.5A, FIG. 5B, and FIG. 5C, which show a diaphragm valve made of resin,such as a non-metallic normally closed diaphragm valve 1 a, which isassembled from a valve portion 10 a and an actuation gas cylinder 10 b,which provide a thermal isolation method. The valve portion 10 aincludes a valve body 2 and a diaphragm 3. The actuation gas cylinder 10b includes an upper valve body 5, a valve upper cover 6, a valve shaft4, an actuation gas connection 171, and a coolant gas connection 161.The actuation gas connection 171 and the coolant gas connection 161 areboth positioned above the heat transfer restriction areas 147. The valveupper cover 6 is gastight disposed on the valve body 2 to form a gascylinder structure 8, the interior of which contains a valve shaft setstructure 7 and springs. The gas cylinder structure 8 is provided with agas chamber 175, and the valve shaft set structure 7 includes thediaphragm 3, the valve shaft 4, and the upper valve body 5. Because ofthe different structures of diaphragm valves, the gas chamber 175 isinstalled on the valve body 2 or the valve upper cover 6.

The valve body 2 includes an annular portion 24 and a square portion 25,wherein the square portion 25 includes an inlet pipe 21, an outlet pipe22, and a valve box 23. The inlet pipe 21 is connected to a pipeconnection 211, and the outlet pipe 22 is connected to a pipe connection221,

The valve box 23 includes a valve seat 231, a flow channel 232, and aflow channel side wall 233, wherein the valve seat 231 is centrallypositioned, the periphery of which forms the circumferentialsymmetrical, indented flow channel 232,

The annular portion 24 is provided with a sealing face 240, an openingportion 241, a minimum diameter area 242, an internal ring surface 243,a seal groove 245, an external ring surface 246, and a heat dissipationribbed plate 248, and is provided with an actuation gas hole 172 and acoolant gas hole 162. The minimum diameter area 242 at one end of theannular portion 24 is connected to the square portion 25. The heatdissipation ribbed plate 248 is installed on the external ring surface246 of the minimum diameter area 242 and connects to the square portion25. The square portion 25, the minimum diameter area 242, the sealgroove 245, and the heat dissipation ribbed plate 248 are all the heattransfer restriction areas 147.

The square portion 25 is provided with a square plate 251 and aplurality of ribbed plates, which includes a plurality of horizontalribbed plates 253, longitudinal vertical ribbed plates 254, and aplurality of transverse vertical ribbed plates 255. An opening in themiddle of the square plate 251 is used to contain the valve box 23, andconnects with the flow channel side wall 233. The longitudinal verticalribbed plates 254 and the transverse vertical ribbed plates 255 areinstalled below the square plate 251 and are used to connect to theinlet pipe 21, the outlet pipe 22, and the flow channel side wall 233.The square plate 251, the longitudinal vertical ribbed plates 254, andthe transverse vertical ribbed plates 255 are all the heat transferrestriction areas 147.

The diaphragm 3 is fitted with a peripheral portion 31, an elastic strip32, and a central portion 33. The center portion 33 is provided with ascrew hole 331.

The valve shaft 4 is fitted with a locking portion 41, a hollow shaftrod 42, and a piston portion 43, wherein the locking portion 41 is usedto tightly lock the central portion 33 of the diaphragm 3. The hollowshaft rod 42 passes through a shaft hole portion 53 of the upper valvebody 5, and is sealed by a plurality of O-shaped rings. The hollow shaftrod 42 is provided with an axis hole 425 and a plurality of gas guideholes 426. The piston portion 43 is fitted with a disc portion 431,lower annular ribbed plates 432, and upper annular ribbed plates 433.The upper annular ribbed plates 433 is installed on the upper side ofthe disc portion 431, and the lower annular ribbed plates 432 isinstalled on the lower portion of the disc portion 431.

The upper valve body 5 is installed on the inner side of the annularportion 24; moreover, the upper valve body 5 is provided with anexternal ring surface 51, a tightening portion 52, the shaft holeportion 53, a first annular recess 54, a second annular recess 55, and adiaphragm chamber 56. The tightening portion 53 is fitted with aplurality of cooling gas guide holes 164 and actuation gas guide holes174. The second annular recess 55 is fitted with a plurality of radialribbed plates 551. The bottom portions of the first annular recess 54and the second annular recess 55 are all the heat transfer restrictionareas 147.

The valve upper cover 6 assumes an inverted cup shape that is assembledon the valve body 2, and is provided with an internal holding chamber61, a top portion 62, an external ring portion 63, and a sealing face64. The internal holding chamber 61 is provided with an internal ringsurface 611, and the top portion 62 is provided with a center throughhole 621 and a plurality of heat dissipation ribbed plates 625.

The pipe connection 211 is assembled on one side of the square portion25. The inlet pipe 21 horizontally passes through one side of the squareportion 25 and connects to the flow channel 232 of the valve seat 231.An opening of the valve seat 231 is used to butt connect with thecentral portion 33 of the diaphragm 3. The entrance of the outlet pipe22 is configured at the flow channel side wall 233 of the valve box 23and penetrates another side of the square portion 25 to connect with thepipe connection 221.

The extension direction of the inlet pipe 21 and the outlet pipe 22defines a horizontal direction. The highest position of the flow channel232 is above the inlet pipe 21 and the outlet pipe 22. The thickness ofthe flow channel side wall 233 is the same as that of the inlet pipe 21.The flow channel side wall 233 is one of the heat transfer restrictionareas 147.

The peripheral portion 31 is fixed in the seal groove 245, andtightening by the tightening portion 52 enables completely sealing thevalve box 23, causing the diaphragm 3 and the minimum diameter area 242to be essentially located at identical horizontal positions. The centralportion 33 acts as a switch corresponding to the valve seat 231.

The gas cylinder structure 8 includes the valve upper cover 6, the uppervalve body 5, and the annular portion 24. The gas chamber 175 isseparated by the piston portion 43 of the valve shaft set structure 7into an upper gas chamber 175 a and a lower gas chamber 175 b. The gaschamber 175 can be installed on the internal ring surface 243 of theannular portion 24, or can be installed on the internal ring surface 611of the internal holding chamber 61 of the valve upper cover 6. The outeredge of the piston portion 43 is coupled to the gas chamber 175 toeffect a reciprocating motion, and the tail end of the valve shaft 4penetrates the center through hole 621 of the valve upper cover 6. Thegas cylinder structure 8 is positioned above the heat transferrestriction areas 147.

The above-described plurality of horizontal ribbed plates 253, thelongitudinal vertical ribbed plates 254, and a plurality of thetransverse vertical ribbed plates 255 connect with the inlet pipe 21,the outlet pipe 22, and the flow channel side wall 233, which do nothave the problem of accumulated thickness 9163 of the prior art.

The lower annular ribbed plates 432 is coupled to the second annularrecess 55, the configuration between the two of which forms a slidingfit, and provides a damping effect to reduce vibration when thediaphragm is being displaced up and down.

The gas cylinder structure 8 is supported by the structure of theannular portion 24, ensuring rigid support of the shaft hole portion 53as well as ensuring perpendicularity and concentricity of the valveshaft 4. The external ring surface 246 fitted with the heat dissipationribbed plates 248 provides additional supporting force for the gascylinder structure 8. Because the external ring surfaces 51 of the uppervalve body 5 are all assembled on the inner side of the annular portion24, thus, the piston portion 43 transmits actuation gas pressure andspring vibration of the gas chamber 175 to the valve body 2, that is,the structure of the valve body 2 is able to absorb and bear thetightening force, and will not produce structural creeping and comeloose. Moreover, the gas cylinder structure 8 is positioned above theheat transfer restriction areas 147, and the upper valve body 5 providedwith the heat transfer restriction areas 147 enables minimizing heattransmission of the heat source areas, which further enables maintainingthe strength of the gas cylinder structure 8.

The annular portion 24 and the valve box 23 construct a cup-shapedstructure 26, which assumes a deep cup shape. The cup-shaped structure26 is provided with an outer edge height 261 (H), which is the heightfrom the seal groove 245 to the sealing face 240. The outer edge height261 (H) is at least 80% to 160% of the height of the upper valve body 5.The diaphragm 3 is assembled at a position close to the bottom portionof the cup-shaped structure 26, wherein this position is also providedwith an internal cooling flow channel to effect cooling. Underconditions of high temperature distortion, the annular portion 24assists in providing high structural strength and also ensuresminimizing the possibility of leakage from the peripheral portion 31 ofthe diaphragm 3. Moreover, the valve shaft set structure 7 is assembledon the annular portion 24, that is, the cup-shaped structure 26 providesthe valve shaft set structure 7 with the most stable support. Hence,concentricity and perpendicularity is ensured when the valve shaft 4 isperforming an opening/closing movement, and maximum assistance toreducing particle release is provided.

A heat dissipation method for the thermal isolation method of thepresent invention comprises an external natural cooling 15 and aninternal cooling 16, wherein the external natural cooling 15 uses thesquare portion 25 of the valve body 2, the heat dissipation ribbedplates 248 of the annular portion 24, and heat dissipation ribbed plates633 of the valve upper cover 6 to carry out natural-convection cooling.The internal cooling 16 is achieved through an internal cooling flowchannel, which includes one or more than one said coolant gas holes 162of the valve body 2, a coolant gas ring groove 163, a plurality of thecoolant gas guide holes 164 of the upper valve body 5, a diaphragm space165 of the diaphragm chamber 56 of the upper valve body 5, a pluralityof the gas guide holes 426 of the valve shaft 4, and the axis hole 425of the hollow shaft rod 42. The internal cooling 16 is separated intointernal natural cooling and internal forced cooling, wherein theinternal natural cooling uses rising force of high temperature gas inthe hollow shaft rod 42 to assist the external cooling gas to enter theinternal cooling flow channel to achieve the objective of expellingquantities of heat. The internal forced cooling consists of externallyforcing cooling gas through the internal cooling flow channel to achievethe objective of expelling quantities of heat. In addition, the squareplate 251 and the horizontal ribbed plates 253, the longitudinalvertical ribbed plates 254, and the transverse vertical ribbed plates255 are all provided with a heat transfer section thickness, which liesbetween 1 centimeter to not exceeding the thicknesses of the inlet pipe21 and the outlet pipe 22, to the extent of being less than 3 mm. Theheat dissipation ribbed plate 625 is provided with a heat transfersection thickness, which lies between 1 centimeter to not exceeding thethicknesses of the inlet pipe 21 and the outlet pipe 22, to the extentof being less than 3 mm. The annular portion 24 is provided with a heattransfer section thickness, and the heat transfer section thickness ofthe minimum diameter area 242 is less than the heat transfer sectionthickness at other positions of the annular portion 24, wherein the heattransfer section thickness of the minimum diameter area 242 lies between1 centimeter to not exceeding the thicknesses of the inlet pipe 21 andthe outlet pipe 22, to the extent of being less than 3 mm. Such aconfiguration enables providing heat dissipation effectiveness andsufficient structural strength.

The different forms of the diaphragm of the present invention includethe non-metallic diaphragm valve 1 a and a metallic diaphragm valve,wherein the non-metallic diaphragm valve 1 a can be separated into anon-metal normally closed diaphragm valve and a non-metallic normallyopen diaphragm valve. The metallic diaphragm valve can be separated intoa metallic normally closed diaphragm valve and a metallic normally opendiaphragm valve. An electrostatic diaphragm valve can be derived fromthe first two types.

The external ring surface 246 of the annular portion 24 of the valvebody 2 is differentiated into a non-metallic annular portion 24 aconfigured with external threaded teeth 247 or a metallic annularportion 24 b configured with a plurality of bolt sleeves 13. The boltsleeves 13 are positioned above the heat transfer restriction areas 147.

The square portion 25 of the valve body 2 is differentiated into a firstmolded square portion 25 a and a second molded square portion 25 b.

The first molded square portion 25 a is consisted of the square plate251, a plurality of the longitudinal vertical ribbed plates 254, aplurality of the horizontal ribbed plates 253, and a plurality of thetransverse vertical ribbed plates 255. The lower structure of the squareplate 251 of the first molded square portion 25 a is used to support theinlet pipe 21, the outlet pipe 22, and the flow channel 232, and furtherconstructs a lattice-shaped ribbed plate with a plurality of horizontalopenings. Moreover, the longitudinal vertical ribbed plates 254 liebelow the square plate 251 and connect the upper sides and lower sidesof the inlet pipe 21 and the outlet pipe 22. The horizontal ribbedplates 253 are on two sides as well as the lower portions of the inletpipe 21, the outlet pipe 22, and the flow channel 232; whereas thetransverse vertical ribbed plates 255 transversely cross over the inletpipe 21, the outlet pipe 22, and the flow channel 232.

The second molded square portion 25 b is consisted of the square plate251 and two of the transverse vertical ribbed plates 255. The lowerstructure of the square plate 251 of the second molded square portion 25b is used to support the inlet pipe 21, the outlet pipe 22, and the flowchannel 232, and further constructs a structure with horizontalopenings. The longitudinal vertical ribbed plates 254 lies below thesquare plate 251 and connects the upper side of the inlet pipe 21 andthe upper side of the outlet pipe 22. The transverse vertical ribbedplate 255 transversely crosses over the lower sides of the inlet pipe 21and the outlet pipe 22. That is, the square portion 25 includes a firstside surface, a second side surface, and a bottom surface, and thelongitudinal vertical ribbed plates 254, the horizontal ribbed plate253, and the transverse vertical ribbed plate 255 form thelattice-shaped ribbed plates on any one of, any two of, or all of thefirst side surface, the second side surface, and the bottom surface.

The valve body 2 is formed by ejection or extrusion molding using PFA(PolyFluoroAlkoxy), in which the lattice-shaped ribbed plates withhorizontal openings are formed from horizontal sliding of two slideblocks. Therefore, the external surfaces of the inlet pipe 21 and theoutlet pipe 22 from the space between a horizontal center line to thesquare plate 251 will not accumulate the PFA material as the accumulatedthickness 9163 of the prior art does. Moreover, the four corners at thelowest side of the square portion 25 can still use four screw caps andbolts to fix the valve body 2 on the mounting plate 10 a 1.

The valve shaft 4 can also be differentiated into a rotatable valveshaft and a fixed valve shaft.

The locking portion 41 of the rotatable valve shaft is provided with abolt hole 411, which is used to fix a bolt 416 therein. After the bolt416 penetrates the bolt hole 411, a screw cap 414 is screwed thereon andthen tightened in the screw hole 331 of the diaphragm 3. The screw cap414 reversely tightens the diaphragm 3; moreover, the external diameterof the bolt 416 is smaller than the diameter of the bolt hole 411 so asto retain a radial clearance.

The locking portion 41 of the fixed valve shaft is provided with athreaded teeth portion 413, which is used to screw tight into the screwhole 331 of the diaphragm 3.

The rotatable valve shaft can be further differentiated into a normallyclosed valve shaft 4 ac and a normally open valve shaft 4 ad, whereinthe lower side of the piston portion 43 of the normally closed valveshaft 4 ac is provided with an additional shock absorption ring 434,which is coupled to the first annular recess 54. The upper side of thepiston portion 43 of the normally closed valve shaft 4 ac is installedwith springs, which ensure that the diaphragm valve is in a normallyclosed state, and the configuration between the two forms a sliding fitthat provides a damping effect to reduce vibration during up and downdisplacement of the diaphragm 3. The lower side of the piston portion 43of the normally open valve shaft 4 ad bears the force of the springsinstalled inside the first annular recess 54 to ensure that thediaphragm valve is in a normally open state.

The fixed valve shaft can be differentiated into a normally closed valveshaft 4 bc and a normally open valve shaft 4 bd, wherein the lower sideof the piston portion 43 of the normally closed valve shaft 4 bc isprovided with the additional shock absorption ring 434, which is coupledto the first annular recess 54. The upper side of the piston portion 43of the normally closed valve shaft 4 bc is installed with springs, whichensure that the diaphragm valve is in a normally closed state, theconfiguration between the two of which forms a sliding fit that providesa damping effect to reduce vibration during up and down displacement ofthe diaphragm 3. The lower side of the piston portion 43 of the normallyopen valve shaft 4 bd bears the force of the springs installed insidethe first annular recess 54 to ensure that the diaphragm valve is in anormally open state.

The upper valve body 5 can be differentiated into an external threadedteeth upper valve body 5 a and a protruding edge upper valve body 5 b.The external ring surface 51 of the external threaded teeth upper valvebody 5 a is configured with the external threaded teeth 511, whereas theexternal ring surface 51 of the protruding edge upper valve body 5 b isconfigured with a radial protruding edge 512.

The valve upper cover 6 can be differentiated into a non-metallic valveupper cover 6 a and a metallic valve upper cover 6 b. The non-metallicvalve upper cover 6 a is configured with internal threaded teeth 632,whereas the metallic valve upper cover 6 b is configured with nointernal threaded teeth 632 but the external ring portion 63 thereof isprovided with a plurality of the bolt sleeves 13.

The valve shaft set structure 7 includes the diaphragm 3, the uppervalve body 5, and the valve shaft 4, and can be differentiated into anexternal threaded teeth valve shaft set 71 and a protruding ring valveshaft set 72. The external threaded teeth valve shaft set 71 uses therotatable valve shaft and the external threaded teeth upper valve body 5a, whereas the protruding ring valve shaft set 72 uses the fixed valveshaft and the protruding edge upper valve body 5 b. Moreover, anelectrostatic valve shaft set 73 can be formed by inserting a conductivefibre 44 into the above-described valve shaft set structure 7, with theconductive fibre 44 passing through the axis hole 425 and then throughthe locking portion 41, finally being fitted to the non-liquid contactside surface of the diaphragm 3 in an annular curved line fashion. Usingthe rotatable valve shaft, the conductive fibre 44 is able to passthrough the radial clearance of the bolt hole 411, whereas using thefixed valve shaft, the conductive fibre 44 is able to pass through thegas guide hole 426.

The gas chamber 175 of the gas cylinder structure 8 is named as anannular gas chamber 176 while being installed on the annular portion 24b, and is named as a valve upper cover gas chamber 177 while beinginstalled on the valve upper cover 6 b. The annular gas chamber 176 mustuse a rotatable valve shaft set, whereas the valve upper cover gaschamber 177, because of its structure, a rotatable valve shaft set or afixed valve shaft set is chosen.

The gas cylinder structure 8 is differentiated into a non-metallic gascylinder structure 8 a and a metallic gas cylinder structure 8 b. Thenon-metallic gas cylinder structure 8 a is lock tightened by usingthreaded teeth between the non-metallic annular portion 24 a and thenon-metallic valve upper cover 6 a, which is also the origin of thenon-metallic diaphragm valve. Each of the four corners of the metallicgas cylinder structure 8 b is tightened and sealed by a metal bolt,which tighten and seal the metallic annular portion 24 b and themetallic valve upper cover 6 b. Each of the bolts is protected by thebolt sleeve 13 that includes an upper bolt sleeve 131 and a lower boltsleeve 132, which is also the origin of the metallic diaphragm valve.

Referring to FIG. 1A, FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D, FIG. 3A, FIG.3C, FIG. 4A, FIG. 5A, which show the first embodiment of the presentinvention, wherein the non-metallic normally closed diaphragm valve 1 amade from fluororesin comprises the valve body 2, an external threadedteeth normally closed valve shaft set 71 a, and the non-metallic valveupper cover 6 a, which are able to provide a practical thermal isolationmethod. The valve body 2 includes the inlet pipe 21, the outlet pipe 22,the valve box 23, the non-metallic annular portion 24 a, and the firstmolded square portion 25 a, wherein the non-metallic annular portion 24a is provided with the annular gas chamber 176. The external threadedteeth normally closed valve shaft set 71 a uses the normally closedvalve shaft 4 ac. The annular portion 24 a, the external threaded teethnormally closed valve shaft set 71 a, and the non-metallic upper cover 6a construct the non-metallic gas cylinder structure 8 a, which is locktightened using threaded teeth of the annular portion 24 a and thenon-metallic upper cover 6 a.

The ribbed plates of the lattice of horizontal openings of the firstmolded square portion 25 a are produced using an injection or extrusionmolded of PFA, with the lattice ribbed plates with horizontal openingsbeing formed by horizontal sliding of two slide blocks. The lowestlayered vertical open-ended lattice ribbed plate is formed by verticalsliding of slide blocks, therefore, the external surfaces of the inletpipe 21 and the outlet pipe 22 from the space between a horizontalcenter line to the square plate 251 will not accumulate the PFA materialas the accumulated thickness 9163 of the prior art does.

The non-metallic annular portion 24 a is provided with the minimumdiameter area 242 at one end connecting to the first square portion 25a, and the external ring surface 246 thereof is fitted with the heatdissipation ribbed plates 248. The seal groove 245 is configured at theminimum diameter area 242. The internal side wall of the seal groove 245is the flow channel side wall 233 while the external side wall is theinternal ring surface 243, and the bottom of the seal groove 245 is thesquare plate 251, which are used to contain the peripheral portion 31 ofthe diaphragm 3 and bear the tightening pressure of the upper valve body5 to achieve sealing effectiveness. When the inlet pipe 21 and theoutlet pipe 22 are full with high temperature, high pressure liquidcausing distortion thereof, separation by the longitudinal verticalribbed plates 254 ensures that the square plate 251 can substantiallyminimize distortion. Moreover, the heat dissipation ribbed plate 248 andthe structure of the minimum diameter area 242, as well as thecup-shaped structure 26 and the outer edge height 261 (H) enablemaintaining the roundness of the seal groove 245.

The external threaded teeth 247 are configured on the external ringsurface of the opening portion 241, and are used to screw tighten thenon-metallic valve upper cover 6 a. The internal ring surface 243 isalso configured with internal threaded teeth 244 and used to screwtighten the external threaded teeth upper valve body 5 a. The externalthreaded teeth 247 overlap the internal threaded teeth 244 by a specificlength, which is at least over and above two tooth spaces of theinternal threaded teeth 244, thereby enabling providing a structure ofhigh strength.

The coolant gas connection 161 and the actuation gas connection 171 arefitted to the upper side of the minimum diameter area 242, with aseparation space positioned on the upper side of the square plate 251,that is, positioned on the upper side of the heat transfer restrictionareas 147. The coolant gas connection 161 is connected to the coolantgas ring groove 163 on the upper side of the seal groove 245 through thecoolant gas hole 162, and serves to cool the peripheral portion 31 ofthe diaphragm 3 to satisfy the needs of high temperature applicationthereof.

The external threaded teeth upper valve body 5 a is provided with aplurality of the cooling gas guide holes 164 that connect to the coolantgas ring groove 163, which are able to ensure non-liquid contact withthe peripheral portion 31 with the diaphragm 3 to achieve adequatecooling. The external ring surface 51 of the external threaded teethupper valve body 5 a is configured with the external threaded teeth 511,which are used to screw tighten on the internal threaded teeth 244 ofthe internal ring surface 243 of the annular portion 24. The externalthreaded teeth upper valve body 5 a are not subjected to the forceapplied by the piston portion 43 and pressure from actuation gas causingdistortion, thereby ensuring concentricity and perpendicularity of thevalve shaft 4, and ensuring the tightening force of the peripheralportion 31 of the diaphragm 3, thus minimizing leakage and extendingserviceable life thereof.

The top portion 62 of the non-metallic valve upper cover 6 a is providedwith the center through hole 621 that holds the tail end of the valveshaft 4 and protrudes therefrom. When the diaphragm 3 rises and opens,the tail end of the valve shaft 4 also rises, enabling operatingpersonnel to visually understand the operating state. The top portion 62is fitted with the heat dissipation ribbed plate 625, and the externalring portion 63 is fitted with the heat dissipation ribbed plate 633.

Referring to FIG. 2D, FIG. 3A, and FIG. 3B, the non-metallic normallyclosed diaphragm valve 2 is provided with the inlet pipe 21, the outletpipe 22, the valve box 23, the non-metallic annular portion 24 a, andthe first molded square portion 25 a. The inlet pipe 21 is connected tothe pipe connection 211, and the outlet pipe 22 is connected to the pipeconnection 221. The valve box 23 includes the valve seat 231, the flowchannel 232, and the flow channel side wall 233. The valve seat 231 iscentrally positioned, the periphery of which forms the circumferentialsymmetrical, indented flow channel 232. The non-metallic annular portion24 a is provided with the sealing face 240, the opening portion 241, theminimum diameter portion 242, the internal ring surface 243, the sealgroove 245, an actuation gas ring groove 173, the coolant gas ringgroove 163, the external ring surface 246, the heat dissipation ribbedplate 248, the external threaded teeth 247, and the internal threadedteeth 244, as well as being provided with the coolant gas hole 162, thecoolant gas connection 161, the actuation gas hole 172, and theactuation gas connection 171. One end of the metallic annular portion 24b is provided with the minimum diameter area 242 connected to the secondmolded square portion 25 b, and is positioned on the outer side of theflow channel 232. The heat dissipation ribbed plate 248 is fitted on theexternal ring surface 246 of the minimum diameter area 242 and connectedto the second molded square portion 25 b. The minimum diameter area 242and the seal groove 245 are both the heat transfer restriction areas147. The first molded square portion 25 a is provided with the squareplate 251, a plurality of the longitudinal vertical ribbed plates 254, aplurality of the transverse vertical ribbed plates 255, and a pluralityof the horizontal ribbed plates 253. The opening in the middle of thesquare plate 251 is used to contain the valve box 23, and connects tothe flow channel side wall 233. The structure on the lower side of thesquare plate 251 is used to support the inlet pipe 21, the outlet pipe22, and the flow channel 232, and further constructs a lattice-shapedribbed plate with a plurality of horizontal openings. The lattice-shapedribbed plate is one of the heat transfer restriction areas 147.Moreover, the longitudinal vertical ribbed plates 254 are positioned atthe lower side of the square plate 251 and connect with the upper sidesand lower sides of the inlet pipe 21 and the outlet pipe 22. Thehorizontal ribbed plates 253 are positioned at two sides and the lowerside of the inlet pipe 21, the outlet pipe 22, and the flow channel 232.The transverse vertical ribbed plates 255 transversely cross over theinlet pipe 21, the outlet pipe 22, and the flow channel 232. The valvebox 23 of the valve body 2 and the non-metallic annular portion 24 aconstruct the cup-shaped structure 26. The cup-shaped structure 26 isprovided with the outer edge height 261 (H), which is the height fromthe seal groove 245 to the sealing face 240; and the outer edge height261 (H) is at least 80% to 160% of the height of the upper valve body 5.

Referring to FIG. 2D, FIG. 3C, and FIG. 5A, wherein FIG. 3C shows anexploded view of the non-metallic normally closed diaphragm valve 2, thenon-metallic normally closed diaphragm valve 2 uses the rotatable valveshaft and the external threaded teeth upper valve body 5 a. The gaschamber 175 installed on the inner side of the non-metallic annularportion 24 a is the annular gas chamber 176. The external threaded teethnormally closed valve shaft set 71 a is assembled from the diaphragm 3,the external threaded teeth upper valve body 5 a, and the normallyclosed valve shaft 4 ac. The normally closed valve shaft 4 ac includesthe locking portion 41, the hollow shaft rod 42, and the piston portion43. The locking portion 41 includes the bolt hole 411, the screw cap414, and the bolt 416. The hollow shaft rod 42 includes the axis hole425 and the gas guide hole 426. The piston portion 43 includes the discportion 431, the lower annular ribbed plates 432, the upper annularribbed plates 433, and the damping ring 434. The external threaded teethupper valve body 5 a includes the external ring surface 51, thetightening portion 52, the shaft hole portion 53, the first annularrecess 54, the second annular recess 55, and the diaphragm chamber 56.The external ring surface 51 is configured with the external threadedteeth 511, and the tightening portion 52 is fitted with the coolant gasguide hole 164 and the actuation gas guide hole 174. The second annularrecess 55 is fitted with a plurality of the radial ribbed plates 551.

Referring to FIG. 4A and FIG. 5A, which show the external threaded teethnormally closed valve shaft set 71 a applied in a non-metallic normallyclosed diaphragm valve using the normally closed valve shaft 4 ac andthe external threaded teeth upper valve body 5 a. The gas chamber 175installed on the inner side of the non-metallic annular portion 24 a isthe annular gas chamber 176. The external threaded teeth normally closedvalve shaft set 71 a is assembled from the diaphragm 3, the externalthreaded teeth upper valve body 5 a, and the normally closed valve shaft4 ac.

Referring to FIG. 4B and FIG. 5B, which show an external threaded teethnormally open valve shaft set 71 b applied in a metallic normally opendiaphragm valve using a rotatable valve shaft and the external threadedteeth upper valve body 5 a. The dissimilarity with FIG. 4A lies in thatthe gas chamber 175 is installed on the metallic valve upper cover 6 band forms the valve upper cover gas chamber 177. The external threadedteeth valve shaft set 71 is assembled from the diaphragm 3, the externalthreaded teeth upper valve body 5 a, and the normally open valve shaft 4ad.

Referring to FIG. 5A, which shows the gas cylinder structure 8 a of theannular gas chamber 176, and uses the external threaded teeth normallyclosed valve shaft set 71 a applied in a non-metallic normally closeddiaphragm valve using the normally closed valve shaft 4 ac and theexternal threaded teeth upper valve body 5 a. The gas chamber 175 isinstalled on the inner side of the non-metallic annular portion 24 a andforms the annular gas chamber 176.

Referring to FIG. 5B, which shows the metallic gas cylinder structure 8b, and uses the external threaded teeth normally closed valve shaft set71 a applied in a metallic normally closed diaphragm valve using thenormally closed valve shaft 4 ac and the external threaded teeth uppervalve body 5 a. The dissimilarities with FIG. 5A lie in that the gaschamber 175 is installed on the inner side of the metallic valve uppercover 6 b and forms the valve upper cover gas chamber 177. The externalthreaded teeth valve shaft set 71 is assembled from the diaphragm 3, theexternal threaded teeth upper valve body 5 a, and the normally closedvalve shaft 4 ac.

Referring to FIG. 1B, FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D, FIG. 3B, FIG.4D, and FIG. 5C, which show a second embodiment of the presentinvention, wherein a metallic normally open diaphragm valve made fromfluororesin comprises the valve body 2, the protruding ring valve shaftset 72, and the metallic valve upper cover 6 b. The valve body 2includes the inlet pipe 21, the outlet pipe 22, the valve box 23, themetallic annular portion 24 b, and the second molded square portion 25b; and is provided with internal cooling. The internal ring surface 243of the metallic annular portion 24 b is used to assemble the protrudingring valve shaft set 72 thereon. The interior of the metallic valveupper cover 6 b is installed with the gas chamber 175. The protrudingring valve shaft set 72 uses the normally open valve shaft 4 bd, theannular portion 24 b, the protruding ring valve shaft set 72, and themetallic valve upper cover 6 b to construct the metallic gas cylinderstructure 8 b. The metallic gas cylinder structure 8 b is tightlyfastened by the metallic annular portion 24 b and the metallic valveupper cover 6 b using metallic bolts; moreover, the protruding ringvalve shaft set 72 is clamped and sealed on the radial protruding edge512 by the metallic annular portion 24 b and the metallic valve uppercover 6 b.

The metallic valve upper cover 6 b assumes a cup shape and is assembledon the metallic annular portion 24 b. The metallic valve upper cover 6 band the protruding ring valve shaft set 72 together with the metallicannular portion 24 b construct the gas cylinder structure 8 b, which isprovided with the valve upper cover gas chamber 177 that is positionedabove the heat transfer restriction areas 147.

The four corner portions of the metallic valve upper cover 6 b and themetallic annular portion 24 b respectively hold the bolt sleeves 13,which are fitted above the minimum diameter area of the annular portion24 and positioned so as to have a space separating them from the squareplate 251, that is, positioned above the heat transfer restriction areas147, thereby preventing the thick and solid structure of the boltsleeves 13 from becoming a large heat transfer area, resulting infailure of heat source separation. The interior of each of the lowerbolt sleeves 132 on the metallic annular portion 24 b is provided with ametallic internal threaded teeth socket, which metal bolts can use totightly fasten and seal the sealing face 240. An upper sealing face 133is provided between the upper bolt sleeves 131 and the lower boltsleeves 132 to prevent the metal bolts from corrosion.

The metallic valve upper cover 6 b and the metallic annular portion 24 bare respectively fitted with a gas column 11 at the side of the inletpipe 21 or the side of the outlet pipe 22, and next to the bolt sleeves13. The coolant gas connection 161 and the actuation gas connection 171are respectively installed on the metallic valve upper cover 6 b,wherein the actuation gas connection 171 communicates directly with thegas chamber 175. The coolant gas hole 162 and the actuation gas hole 172are provided on the valve upper cover 6 and the annular portion 24,respectively. Two gas columns 169 on a sealing face 113 are also eachinstalled with an O-shaped ring to seal and ensure gas tightness.Moreover, the gas columns 169 are installed above the minimum diameterarea of the annular portion 24 and positioned so as to have a spaceseparating them from the square plate 251, that is, positioned above theheat transfer restriction areas 147, thereby preventing the thick andsolid structure of the gas columns 169 from becoming large heat transferareas, resulting in failure of heat source separation.

Actuation gas is actuated by passing through the actuation gasconnection 171 to the upper side of the piston 43. The outer edge of thepiston 43 is coupled to the gas chamber 175 to effect a reciprocatingmotion.

The internal cooling 16 uses internal forced cooling 16 b, wherein thecoolant gas passes through the coolant gas connection 161, then throughthe coolant gas hole 162 and enters the coolant gas ring groove 163;thereon the coolant gas passes through a plurality of the coolant gasguide holes 164 and enters the non-liquid contact side of the diaphragm3 of the diaphragm space 165, finally passing through the gas guideholes 426 to enter an axis hole 167, and expelled from a gas recoveryconnection 168. The internal forced cooling 16 b carries out bettercooling of the peripheral portion 31 of the diaphragm 3, and thus isable to maintain the tightening force of the tightening portion 52.Moreover, the heat will not easily dissipate outward from thefluororesin O-rings on the valve shaft 4 and the piston portion 43 butis able to dissipate through a hollow axis channel 158, ensuring bothconcentricity and perpendicularity of the valve shaft 4.

The tightening and sealing effectiveness of the present inventionensures high structural strength, resistance to surrounding corrosivegas, and endurance to the reciprocating motion of a piston.

Regarding the structural strength, the gas cylinder structure, the fourbolt sleeves 13 and the gas columns 11 are all positioned above theminimum diameter area 242 of the annular portion 24, and also positionedabove the square plate 51, as well as being positioned above the heattransfer restriction areas 147. Actuation gas pressure from pistonmovement and vibrations from the springs 12 are all transferred to thevalve body 2, the structure of which is able to absorb and endure.

Regarding resistance to surrounding corrosive gas, the cup-shapedstructure 26 and the upper edge height 261 (H) enable distancing themetallic bolts from the position of the diaphragm 3, thereby reducingmicro amounts of gas from penetrating the diaphragm 3 or corrosion fromliquid entering, thus removing contamination problems from metallicoxide diffusion, and eliminating the need for operators and inspectorsto inspect whether or not the bolts are corroded and need replacing.

Regarding endurance to the reciprocating motion of a piston, thecup-shaped structure 26 and the upper edge height 261 (H) ensure firmsupport of the protruding edge upper valve body 5 b. The protruding edgeupper valve body 5 b is not subjected to the force applied by the pistonportion 43 and the pressure of the actuation gas, but provides atightening force with high dependability to seal and minimize structuraldistortion and creeping. Further, the protruding edge upper valve body 5b will not reduce the tightening force and cause leakage from thediaphragm 3, thus ensuring concentricity and perpendicularity of thevalve shaft, as well as ensuring the tightening force of the peripheralportion 31 of the diaphragm 3, thereby minimizing leakage and extendingthe serviceable life thereof.

Referring to FIG. 3B, which shows the valve body 2 applied in a metallicnormally open diaphragm valve, wherein the valve body 2 is provided withthe inlet pipe 21, the outlet pipe 22, the valve box 23, the metallicannular portion 24 b, and the second molded square portion 25 b. Theinlet pipe 21 is connected to the pipe connection 211, and the outletpipe 22 is connected to the pipe connection 221. The valve box 23includes the valve seat 231, the flow channel 232, and the flow channelside wall 233. The valve seat 231 is centrally positioned, the peripheryof which forms the circumferential symmetrical, indented flow channel232. The metallic annular portion 24 b is provided with the sealing face240, the opening portion 241, the minimum diameter area 242, theinternal ring surface 243, the seal groove 245, the coolant gas ringgroove 163, the external ring surface 246, the heat dissipation ribbedplate 248, a lower gas column 112, and a plurality of the lower boltsleeves 132; as well as further provided with the coolant gas hole 162.The minimum diameter area 242 provided at one end of the annular portion24 is connected to the second molded square portion 25 b, and ispositioned on the outer side of the flow channel 232. The heatdissipation ribbed plate 248 is fitted on the external ring surface 246of the minimum diameter area 242 and connected to the second moldedsquare portion 25 b. The minimum diameter area 242 and the seal groove245 are both the heat transfer restriction areas 147. The second moldedsquare portion 25 b is provided with the square plate 251, a pluralityof the longitudinal vertical ribbed plates 254, and a plurality of thetransverse vertical ribbed plates 255. An opening in the middle of thesquare plate 252 is used to contain the valve box 23, and connects tothe flow channel side wall 233. The longitudinal vertical ribbed plates254 are installed on the lower side of the square plate 251, and areused to connect to the upper sides of the inlet pipe 21 and the outletpipe 22, and connect to the flow channel side wall 233. The square plate251 and the longitudinal vertical ribbed plates 254 are all the heattransfer restriction areas 147. The valve box 23 of the valve body 2 andthe metallic annular portion 24 b construct the cup-shaped structure 26.The cup-shaped structure 26 is provided with the outer edge height 261(H), the height of which is from the seal groove 245 to the sealing face240. The outer edge height 261 (H) is at least 80% to 160% of the heightof the upper valve body 5, Referring to FIG. 4C, which shows aprotruding edge normally closed valve shaft set 72 a applied in ametallic normally closed diaphragm valve using the fixed normally closedvalve shaft 4 bc and the protruding edge upper valve body 5 b. The gaschamber 175 is installed on the inner side of the non-metallic annularportion 24 a and forms the annular gas chamber 176. The externalthreaded teeth valve shaft set 71 a is assembled from the diaphragm 3,the protruding edge upper valve body 5 b, and the fixed normally closedvalve shaft 4 bc.

Referring to FIG. 4D, which shows the protruding ring valve shaft set72, applied in the metallic normally open diaphragm valve using thenormally open valve shaft 4 bd and the protruding edge upper valve body5 b. The external threaded teeth valve shaft set 71 is assembled fromthe diaphragm 3, the protruding edge upper valve body 5 b, and thenormally open valve shaft 4 bd.

Referring to FIG. 4E, which shows the electrostatic valve shaft set 73,wherein a conductive fibre 44 is inserted into the protruding ring valveshaft set 72. The conductive fibre 44 passes through the axis hole 425,and then through the radial clearance of the bolt hole 411 of therotatable valve shaft 4 a. The conductive fibre 44 is then fitted to thenon-liquid contact side surface of the diaphragm 3 in an annular curvedline fashion, and further connected to an external earth connection. Theconductive fibre 44 is not affected by rotation of the valve shaft 4.The present invention can also use the normally open valve shaft 4 bd,wherein the conductive fibre 44 passes through the axis hole 425, andthen passes through the gas guide hole 426 of the fixed valve shaft. Theconductive fibre 44 is then fitted to the non-liquid contact sidesurface of the diaphragm 3 in an annular curved line fashion, andfurther connected to an external earth connection.

Referring to FIG. 5C, which shows the gas cylinder structure of thevalve upper cover gas chamber, and uses the protruding ring valve shaftset 72 for application in the metallic normally open diaphragm valveusing the normally closed valve shaft 4 bc and the protruding edge uppervalve body 5 b. The gas chamber 175 is installed on the inner side ofthe metallic valve upper cover 6 b and forms the valve upper cover gaschamber 177. The protruding ring valve shaft set 72 is assembled fromthe diaphragm 3, the protruding edge upper valve body 5 b, and thenormally closed valve shaft 4 bc.

It is of course to be understood that the embodiments described hereinare merely illustrative of the principles of the invention and that awide variety of modifications thereto may be effected by persons skilledin the art without departing from the spirit and scope of the inventionas set forth in the following claims.

What is claimed is:
 1. A diaphragm valve structure, which satisfies the requirements for application in an corrosive operating environment and at a high temperature of 200° C., and is suitable for non-metallic diaphragm valves and metallic diaphragm valves; comprising a valve portion and an actuation gas cylinder, wherein the valve portion includes a fluororesin valve body and a fluororesin diaphragm; the actuation gas cylinder includes an upper valve body, a valve upper cover, a valve shaft, an actuation gas connection, and a coolant gas connection; the diaphragm includes a peripheral portion, an elastic strip, and a central portion; the valve body includes an annular portion and a square portion, wherein the square portion is provided with an inlet pipe, an outlet pipe, and a valve box, wherein the valve box includes a valve seat and a flow channel; the annular portion forms an open ring structure, including a sealing face, an opening portion, an internal ring surface, and an external ring surface, wherein the internal ring surface includes a seal groove and an O-ring groove; the upper valve body includes an external ring surface, an internal ring surface, a tightening portion, a shaft hole portion, and a diaphragm chamber; the upper valve body is installed inside the annular portion, the tightening portion is used to tighten the peripheral portion of the diaphragm into the seal groove of the annular portion; the valve shaft includes a locking portion, a hollow shaft rod, an axis hole, and a piston portion, wherein the locking portion is used to tightly lock the central portion of the diaphragm; the hollow shaft rod passes through the shaft hole portion of the upper valve body, and is sealed by a plurality of O-rings; the valve upper cover includes an internal holding chamber, a top portion, a center through hole, an external ring surface, and a sealing face, wherein the valve upper cover is airtight disposed on the valve body to form an gas cylinder structure, which is provided with a gas chamber; the gas chamber is separated by a piston to form an upper gas chamber and a lower gas chamber; the diaphragm, the valve shaft, and the upper valve body are assembled to form a valve shaft set structure; the tail end of the valve shaft penetrates a center through hole of the valve upper cover, the annular portion and the valve box construct a cup-shaped structure, wherein the valve shaft set structure and the gas cylinder structure are supported by the cup-shaped structure; heat source areas, the heat source areas includes a valve box heat source area, a flow channel heat source area, an inlet pipe heat source area, and an outlet pipe heat source area; the square portion, the annular portion, the upper valve body, and the diaphragm form heat transfer paths; the square portion includes a square plate and a plurality of ribbed plates, the ribbed plates are connected to the lower side of the square plate and also connect with the side walls of the inlet pipe and the outlet pipe, and further connect with the side wall of the flow channel; heat transfer restriction areas include the square plate and the ribbed plates, the heat transfer restriction areas are provided with a heat transfer section thickness, the heat transfer section thickness does not exceed or equals the thickness of the inlet pipe, to the extent of being less than 3 mm; an opening in the middle of the square plate is used to contain the valve box and connect with the side wall of the flow channel; a minimum diameter area of the annular portion connects with the upper side of the square plate, the external side wall of the seal groove is the internal ring surface of the annular portion, and the internal side wall of the seal groove is the side wall of the flow channel; the bottom portion of the seal groove is the square plate, heat transfer restriction areas also include the seal groove and the minimum diameter area of the annular portion; the external ring surface is fitted with a plurality of heat dissipation ribbed plates connected to the square plate, the heat transfer restriction areas also include the heat dissipation ribbed plates; the plurality of heat dissipation ribbed plates include a plurality of external natural cooling structures and internal cooling structures; the natural cooling structures include the exterior surface of the square portion, the heat dissipation ribbed plates of the annular portion and a plurality of valve upper cover ribbed plates, which provide natural-convection cooling; the internal cooling structure achieves a cooling effect by passing a coolant gas through a gas coolant flow channel, wherein the gas coolant flow channel includes one or more than one coolant gas hole in the annular portion, and the coolant gas holes afford passage to a coolant gas ring groove, the coolant gas ring groove further connects with a plurality of coolant gas guide holes on the tightening portion of the upper valve body; the coolant gas guide holes afford passage to a non-liquid contact side of the diaphragm chamber, the coolant gas further passes through the plurality of coolant gas guide holes of the hollow shaft rod that connect with the axis hole.
 2. The diaphragm valve structure according to claim 1, wherein the diameter of the opening of the valve box is one inch, the heat transfer section thickness of the heat transfer restriction areas is greater than 1 mm.
 3. The diaphragm valve structure according to claim 1, wherein the gas cylinder structure includes a part of the annular portion, the gas cylinder structure is positioned above the square plate and the heat transfer restriction areas of the annular portion.
 4. The diaphragm valve structure according to claim 1, wherein the extension directions of the inlet pipe and the outlet pipe are in a horizontal direction, the square portion includes the square plate, a plurality of horizontal ribbed plates, a plurality of longitudinal vertical ribbed plate, and a plurality of transverse vertical ribbed plates, which are inter-connected to construct a horizontal lattice-shaped ribbed plate structure with horizontal openings.
 5. The diaphragm valve structure according to claim 4, wherein the square portion connects with the valve box heat source area, the flow channel heat source area, the inlet pipe heat source area, and the outlet pipe heat source area; the horizontal ribbed plates are positioned at two sides and the lower side of the inlet pipe, the outlet pipe, and the flow channel, the transverse vertical ribbed plates transversely cross over the lower side of the square plate and the inlet pipe, the outlet pipe, and the flow channel.
 6. The diaphragm valve structure according to claim 1, wherein the heat transfer restriction areas include the periphery of the valve box heat source area, which includes the minimum diameter area of the annular portion, the side wall of the flow channel of the valve box, and the square plate.
 7. The diaphragm valve structure according to claim 1, wherein the upper valve body is provided with a first annular recess and a second annular recess, the heat transfer restriction areas include the bottom portions of the first annular recess and the second annular recess of the upper valve body.
 8. The diaphragm valve structure according to claim 1, the internal cooling structure adopts internal natural cooling that uses the rising force of high temperature coolant gas in the hollow shaft rod to assist the entry of external coolant gas from the gas coolant flow channel, which then passes through the hollow shaft rod, from which hot gas is expelled.
 9. The diaphragm valve structure according to claim 1, the internal cooling structure adopts internal forced cooling that consists of externally forcing high pressure coolant gas from the coolant gas connection to enter the valve structure by passing through the gas coolant flow channel, and then passes through the hollow shaft rod, from which hot gas is expelled, to achieve the internal forced cooling.
 10. The diaphragm valve structure according to claim 1, wherein the coolant gas ring groove is installed on the internal ring surface of the annular portion.
 11. The diaphragm valve structure according to claim 1, wherein the coolant gas ring groove is installed on the external ring surface of the upper valve body.
 12. The diaphragm valve structure according to claim 1, wherein the upper side of the coolant gas ring groove is installed with an O-ring that isolates the high pressure gas.
 13. The diaphragm valve structure according to claim 1, wherein the coolant gas connection is installed on the annular portion, and the coolant gas connection is positioned above the minimum diameter area of the annular portion and the square plate constructed heat transfer restriction areas.
 14. The diaphragm valve structure according to claim 1, wherein the actuation gas connection is installed on the annular portion, and the actuation gas connection is positioned above the minimum diameter area of the annular portion and the square plate constructed heat transfer restriction areas.
 15. The diaphragm valve structure according to claim 1, wherein the gas cylinder structure uses a plurality of bolt sleeves and a plurality of metal bolts for tightly locking and sealing thereof, the bolt sleeves and the metal bolts are positioned above the minimum diameter area of the annular portion and the square plate constructed heat transfer restriction areas.
 16. The diaphragm valve structure according to claim 1, wherein the coolant gas connection is installed on the valve upper cover, and a plurality of gas columns on the outer side of the gas cylinder structure are positioned above the minimum diameter area of the annular portion and the square plate constructed heat transfer restriction areas.
 17. The diaphragm valve structure according to claim 1, wherein the actuation gas connection is installed on the valve upper cover, and the plurality of gas columns on the outer side of the gas cylinder structure are positioned above the minimum diameter area of the annular portion and the square plate constructed heat transfer restriction areas. 